Air-conditioning apparatus

ABSTRACT

A controller, at least during the heating operation, controls the opening degree of a second expansion device and/or a third expansion device based on a discharge refrigerant temperature detected by a discharge refrigerant temperature detector, or a value computed using the discharge refrigerant temperature, and causes refrigerant having a quality equal to or greater than 0.9 and less than or equal to 0.99 to be suctioned into a compressor.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a U.S. national stage application of InternationalApplication No. PCT/JP2012/080136, filed on Nov. 21, 2012, the contentof which is incorporated herein by reference.

TECHNICAL FIELD

The present invention relates to an air-conditioning apparatus appliedto a multi-air conditioning system for a building, for example.

BACKGROUND

A refrigeration device has been proposed in which a liquid receiver isconnected to the downstream side of a condenser, and liquid refrigerantcollected by the liquid receiver is supplied to a compressor via aliquid injection circuit to lower the temperature of dischargerefrigerant from the compressor (for example, see Patent Literature 1).

The technique described in Patent Literature 1 detects the temperatureof discharge refrigerant from the compressor, and varies the openingdegree of a flow control valve according to the detected temperature tocontrol the injection flow rate.

In addition, heat pump air conditioners equipped with a four-way valvethat switch between cooling and heating by reversing the flow ofrefrigerant have been variously proposed (for example, see PatentLiterature 2).

In the technique described in Patent Literature 2, an injection pipe isconnected between a compressor and a pipe connecting an indoor heatexchanger to an outdoor heat exchanger, thereby enabling liquidrefrigerant flowing through the pipe to be supplied to the compressor.

Furthermore, an air-conditioning apparatus equipped with a plurality ofsolenoid valves and able to perform a cooling and heating mixedoperation in addition to cooling and heating has been proposed (forexample, see Patent Literature 3).

In the technique described in Patent Literature 3, for injection duringheating, an expansion device is provided on an injection circuit toinject refrigerant at an intermediate pressure (hereinafter designatedintermediate pressure refrigerant) into a compressor.

In this way, the technologies described in Patent Literature 1 to 3inject liquid refrigerant into a compressor and lower the temperature ofdischarge refrigerant from the compressor in order to minimize damage tothe compressor.

PATENT LITERATURE

-   Patent Literature 1: Japanese Unexamined Patent Application    Publication No. 7-260262 (for example, see FIG. 1)-   Patent Literature 2: Japanese Unexamined Patent Application    Publication No. 8-210709 (for example, see FIG. 1)-   Patent Literature 3: Japanese Unexamined Patent Application    Publication No. 2010-139205 (for example, see FIG. 1)

The refrigeration device in Patent Literature 1 performs injection whenthe flow direction of refrigerant is flowing in a first direction, andis not assumed injection when the flow direction of refrigerant isreversed, for example. Also, for the air-conditioning apparatusdescribed in Patent Literature 2, although injection may still beperformed even when the flow direction of refrigerant is reversed,injecting while performing the cooling and heating mixed operation isnot assumed.

In other words, the technologies described in Patent Literature 1 and 2are problematic in that the operation modes when conducting injectionare limited, and to that extent, there is a possibility of conveniencebeing impaired.

The technique described in Patent Literature 3 is able to inject duringcooling, heating, as well as the cooling and heating mixed operation,but since the opening degree of the expansion device on the injectioncircuit is not specified, the pressure of the intermediate pressurerefrigerant is not varied according to the situation.

In other words, the technique described in Patent Literature 3 isproblematic in that the pressure of the intermediate pressurerefrigerant is not controlled according to the operation mode, and thusdamage to the compressor is more likely to occur, while the stabilityand reliability of the operation of the air-conditioning apparatus islowered.

SUMMARY

The present invention solves the above problems, and takes as anobjective to provide a highly reliable air-conditioning apparatus thatimproves operating stability by lowering the temperature of dischargerefrigerant from a compressor, irrespective of operation mode.

An air-conditioning apparatus according to the present inventionincludes a compressor, a refrigerant flow switching device, a first heatexchanger, a first expansion device, and a second heat exchangerconnected via refrigerant pipes, and constitutes a refrigerant circuit,the air-conditioning apparatus being provided with: a second expansiondevice provided on an upstream side of the first heat exchanger duringthe heating operation; an accumulator for accumulating excessrefrigerant provided on an upstream side of the compressor; a suctioninjection pipe, having one end connected on an upstream side of thesecond expansion device during the heating operation, and another endconnected to a flow channel between a suction side of the compressor andthe accumulator; a third expansion device provided to the suctioninjection pipe; a discharge refrigerant temperature detector thatdetects a discharge refrigerant temperature of the compressor; and acontroller that controls an opening degree of the second expansiondevice and/or the third expansion device based on at least a detectionresult from the discharge refrigerant temperature detector. Inside therefrigerant pipes, a refrigerant having a higher discharge refrigeranttemperature than R410A is circulated as refrigerant. At least during theheating operation, the controller controls the opening degree of thesecond expansion device and/or the third expansion device based on thedischarge refrigerant temperature detected by the discharge refrigeranttemperature detector, or a value computed using the dischargerefrigerant temperature, and causes refrigerant having a quality equalto or greater than 0.9 and less than or equal to 0.99 to be suctionedinto the compressor.

Since an air-conditioning apparatus according to the present inventionhas the above configuration, it is possible to obtain a highly reliableair-conditioning apparatus that improves operating stability by loweringthe temperature of discharge refrigerant from a compressor, irrespectiveof operation mode.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic diagram illustrating an exemplary installation ofan air-conditioning apparatus according to Embodiment 1 of the presentinvention.

FIG. 2 is an exemplary circuit layout of the air-conditioning apparatusaccording to Embodiment 1 of the present invention.

FIG. 3 is a diagram explaining the flow of refrigerant and heat mediumduring a cooling only operation of the air-conditioning apparatusillustrated in FIG. 2.

FIG. 4 is a pressure-enthalpy chart (p-h chart) during the cooling onlyoperation illustrated in FIG. 3.

FIG. 5 is a diagram explaining the flow of refrigerant and heat mediumduring a heating only operation of the air-conditioning apparatusillustrated in FIG. 2.

FIG. 6 is a p-h chart during the heating only operation illustrated inFIG. 5.

FIG. 7 is a diagram explaining the flow of refrigerant and heat mediumduring cooling main operation of the air-conditioning apparatusillustrated in FIG. 2.

FIG. 8 is a p-h chart during the cooling main operation illustrated inFIG. 7.

FIG. 9 is a diagram explaining the flow of refrigerant and heat mediumduring the heating only operation of the air-conditioning apparatusillustrated in FIG. 2.

FIG. 10 is a p-h chart during the heating main operation illustrated inFIG. 9.

FIG. 11 is a flowchart illustrating the operation of medium pressurecontrol, activation control, and steady-state control of theair-conditioning apparatus according to Embodiment 1 of the presentinvention.

FIG. 12 is a flowchart illustrating the operation of medium pressurecontrol of the air-conditioning apparatus according to Embodiment 1 ofthe present invention.

FIG. 13 is a flowchart illustrating the operation of stead-state controlof the air-conditioning apparatus according to Embodiment 1 of thepresent invention.

FIG. 14 is a graph for explaining three-point prediction.

FIG. 15 is a flowchart illustrating the operation of activation controlof the air-conditioning apparatus according to Embodiment 1 of thepresent invention.

FIG. 16 is a graph illustrating the state of an end determination flagused in activation control of the air-conditioning apparatus accordingto Embodiment 1 of the present invention.

FIG. 17 is an explanatory diagram of a circuit layout that differs fromthe exemplary circuit layout illustrated in FIG. 2.

FIG. 18 is a flowchart illustrating the operation of activation controlof the air-conditioning apparatus according to Embodiment 2 of thepresent invention.

FIG. 19 is a flowchart illustrating the operation of activation controlof the air-conditioning apparatus according to Embodiment 3 of thepresent invention.

FIG. 20 is a computational flowchart for computing the quality ofrefrigerant suctioned into a compressor of the air-conditioningapparatus according to Embodiment 4 of the present invention.

FIG. 21 is a graph illustrating the viscosity behavior of a mixture ofrefrigerant and refrigerating machine oil.

DETAILED DESCRIPTION Embodiment 1

An embodiment of the present invention will be described on the basis ofthe drawings. FIG. 1 is a schematic diagram illustrating an exemplaryinstallation of an air-conditioning apparatus according to the presentembodiment. An exemplary installation of the air-conditioning apparatuswill be described on the basis of FIG. 1. With the presentair-conditioning apparatus, each indoor unit is able to freely select acooling mode or a heating mode as the operation mode by utilizingrefrigeration cycles (a refrigerant circuit A and a heat medium circuitB) that circulate a refrigerant and a heat medium. Note that, in thedrawings hereinafter, including FIG. 1, the relative sizes of respectivestructural members may differ from actual sizes in some cases.

In FIG. 1, the air-conditioning apparatus according to the presentembodiment is equipped with one outdoor unit 1 which is the heat sourceunit, multiple indoor units 2, and a heat medium relay unit 3 interposedbetween the outdoor unit 1 and the indoor units 2. The heat medium relayunit 3 exchanges heat between the refrigerant (heat source siderefrigerant) and the heat medium. The outdoor unit 1 and the heat mediumrelay unit 3 are connected by refrigerant pipes 4 that conduct therefrigerant. The heat medium relay unit 3 and the indoor units 2 areconnected by pipes (heat medium pipes) 5 that conduct the heat medium.Also, cooling energy or heating energy generated at the outdoor unit 1is transferred to the indoor units 2 via the heat medium relay unit 3.

The outdoor unit 1 is ordinarily placed in an outdoor space 6, which isa space outside a building or other facility 9 (such as the roof, forexample), and provides cooling energy or heating energy to the indoorunits 2 via the heat medium relay unit 3. The indoor units 2 aredisposed at positions able to supply cooled air or heated air to anindoor space 7, which is a space inside the facility 9 (such as a room,for example), and provide cooled air or heated air to the indoor space 7or air-conditioned space. The heat medium relay unit 3 is configured asa separate housing from the outdoor unit 1 and the indoor units 2 ableto be installed in a separate location from the outdoor space 6 and theindoor space 7, is connected to the outdoor unit 1 and the indoor units2 by the refrigerant pipe 4 and the heat medium pipes 5, respectively,and conveys cooling energy or heating energy supplied from the outdoorunit 1 to the indoor units 2.

As illustrated in FIG. 1, in the air-conditioning apparatus according tothe present embodiment, the outdoor unit 1 and the heat medium relayunit 3 are connected using two refrigerant pipes 4, while the heatmedium relay unit 3 and each of the indoor units 2 are connected by twopipes 5. In this way, by using two pipes (the refrigerant pipes 4 andthe pipes 5) to connect each unit (the outdoor unit 1, the indoor units2, and the heat medium relay unit 3) in the air-conditioning apparatusaccording to the present embodiment, construction becomes facilitate.

Note that FIG. 1 illustrates, as an example, a state in which the heatmedium relay unit 3, although inside the facility 9, is installed in aspace which is a separate space from the indoor space 7, such as abovethe ceiling (hereinafter simply designated the space 8). The heat mediumrelay unit 3 is otherwise installable in a shared space containing anelevator or the like. Also, although FIGS. 1 and 2 illustrate the casein which the indoor units 2 are ceiling cassettes as an example, theconfiguration is not limited thereto, and the indoor units 2 may be ofany type, such as ceiling-concealed or ceiling-hung units, insofar asthe indoor units 2 are able to expel heated air or cooled air into theindoor space 7 directly or via means such as ducts.

Although FIG. 1 illustrates the case of the outdoor unit 1 beinginstalled in the outdoor space 6 as an example, the configuration is notlimited thereto. For example, the outdoor unit 1 may also be installedin an enclosed space such as a ventilated machine room, and may beinstalled inside the facility 9 insofar as waste heat can be exhaustedoutside the facility 9 by an exhaust duct. Alternatively, the outdoorunit 1 may be installed inside the facility 9 using a water-cooledoutdoor unit 1. Installing the outdoor unit 1 in any such location isnot particularly problematic.

It is also possible to install the heat medium relay unit 3 near theoutdoor unit 1. However, the heat medium pumping power will be verylarge if the distance from the heat medium relay unit 3 to the indoorunits 2 is too long, and thus care must be taken not to squander theenergy-saving advantages. Furthermore, the number of connected outdoorunits 1, indoor units 2, and heat medium relay units 3 is not limited tothe numbers illustrated in FIGS. 1 and 2, and it is sufficient todetermine numbers according to the facility 9 where the air-conditioningapparatus according to the present embodiment is installed.

FIG. 2 is an exemplary circuit layout of an air-conditioning apparatus(hereinafter designated the air-conditioning apparatus 100) according tothe present Embodiment 1. A detailed configuration of theair-conditioning apparatus 100 will be described on the basis of FIG. 2.

As illustrated in FIG. 2, the outdoor unit 1 and the heat medium relayunit 3 are connected by refrigerant pipes 4 via an intermediate heatexchanger 15 a and an intermediate heat exchanger 15 b provided in theheat medium relay unit 3. Also, the heat medium relay unit 3 and theindoor units 2 are likewise connected by the pipes 5 via theintermediate heat exchanger 15 a and the intermediate heat exchanger 15b. Note that the refrigerant pipes 4 will be further discussed at alater stage.

The air-conditioning apparatus 100 includes a refrigerant circuit A,which is a refrigeration cycle that circulates a refrigerant, as well asa heat medium circuit B that circulates a heat medium. Each of theindoor units 2 is able to select between a cooling operation and aheating operation. Additionally, it is possible to conduct a coolingonly operation mode, which is a mode in which all operating indoor units2 execute the cooling operation, a heating only operation mode, which isa mode in which all indoor units 2 execute the heating operation, and acooling and heating mixed operation mode, which is a mode in whichindoor units execute a mix of the cooling operation and heatingoperation. Note that the cooling and heating mixed operation modeincludes a cooling main operation mode in which the cooling load isgreater, and a heating main operation mode in which the heating load isgreater. The cooling only operation mode, the heating only operationmode, the cooling main operation mode, and the heating main operationmode will be described in detail with the description of FIGS. 3 to 10.

[Outdoor Unit 1]

The outdoor unit 1 is equipped with a compressor 10, a first refrigerantflow switching device 11 such as a four-way valve, a heat source sideheat exchanger 12, and an accumulator 19, which are connected in seriesby the refrigerant pipes 4.

The outdoor unit 1 is also provided with a first connecting pipe 4 a, asecond connecting pipe 4 b, a check valve 13 a, a check valve 13 b, acheck valve 13 c, and a check valve 13 d.

Furthermore, the outdoor unit 1 is equipped with a branching unit 27 a,a branching unit 27 b, an opening and closing device 24, a backflowprevention device 20, an expansion device 14 a, an expansion device 14b, a medium pressure detection device 32, a discharge refrigeranttemperature detection device 37, a suction refrigerant temperaturedetection device 38, a branch refrigerant temperature detection device33, a high pressure detection device 39, a suction pressure detectiondevice 60, a compressor shell temperature detection device 61, a suctioninjection pipe 4 c, a branch pipe 4 d, and a controller 50.

The compressor 10 suctions refrigerant and compresses the refrigerant toa high temperature, high pressure state. The compressor 10 may beconfigured as a variable-capacity inverter compressor or the like, forexample. The discharge side of the compressor 10 is connected to thefirst refrigerant flow switching device 11, while the suction side isconnected to the suction injection pipe 4 c and the accumulator 19. Thecompressor 10 is a low-pressure shell-type compressor, which alsoincludes a compression chamber inside a hermetically sealed container,in which the inside of the hermetically sealed container is in alow-pressure refrigerant pressure environment, and that suctions andcompresses low-pressure refrigerant inside the hermetically sealedcontainer into the compression chamber. In addition, the compressor 10is connected to the suction injection pipe 4 c connected to therefrigerant pipe 4 between the suction side of the compressor 10 and theaccumulator 19, making it possible to supply high pressure or mediumpressure refrigerant to the suction injection pipe 4 c.

In the lower part of the compressor 10, refrigerant and oil(refrigerating machine oil) flowing in from the suction side of thecompressor 10 is able to flow in. Also, the compressor 10 includes amiddle part where a motor is disposed, in which the refrigerant flowingin from the lower part of the compressor 10 is compressed. Furthermore,in the upper part of the compressor 10, a discharge chamber made up of ahermetically sealed container is provided, making it possible todischarge the refrigerant and oil compressed in the middle part. In thisway, the compressor 10 includes a portion exposed to high temperatureand high pressure refrigerant as in the upper part of the compressor 10,and a portion exposed to low temperature and low pressure refrigerant asin the lower part of the compressor 10, and thus the temperature of thehermetically sealed container constituting the compressor 10 becomes anintermediate temperature therebetween. Note that while the compressor 10is operating, the motor generates heat due to an electric currentsupplied to the motor in the middle part. Consequently, the lowtemperature and low pressure two-phase gas-liquid refrigerant suctionedinto the compressor 10 is heated by the hermetically sealed containerand the motor of the compressor 10.

The first refrigerant flow switching device 11 switches between a flowof refrigerant during a heating operation (during the heating onlyoperation mode and during the heating main operation mode discussedlater) and a flow of refrigerant during the cooling operation (duringthe cooling only operation mode and during the cooling main operationmode discussed later). Note that FIG. 2 illustrates a state in which thefirst refrigerant flow switching device 11 is connected to the dischargeside of the compressor 10 and the first connecting pipe 4 a, andconnected to the heat source side heat exchanger 12 and the accumulator19.

The heat source side heat exchanger 12 functions as an evaporator duringthe heating operation, functions as a condenser (or radiator) during thecooling operation, and exchanges heat between the refrigerant and airsupplied from an air-sending device such as a fan (not illustrated),causing that the refrigerant to evaporate and gasify or condense andliquefy. One side of the heat source side heat exchanger 12 is connectedto the first refrigerant flow switching device 11, while the other sideis connected to the refrigerant pipe 4 on which the check valve 13 a isprovided.

The accumulator 19 is provided on the suction side of the compressor 10,and accumulates excess refrigerant. One side of the accumulator 19 isconnected to the first refrigerant flow switching device 11, while theother side is connected to the suction side of the compressor 10.

The check valve 13 a is provided on a refrigerant pipe 4 between theheat source side heat exchanger 12 and the heat medium relay unit 3, andallows the flow of refrigerant only in a designated direction (thedirection from the outdoor unit 1 to the heat medium relay unit 3). Thecheck valve 13 b is provided on the first connecting pipe 4 a, andcauses the refrigerant discharged from the compressor 10 during theheating operation to circulate only in the direction towards the heatmedium relay unit 3. The check valve 13 c is provided on the secondconnecting pipe 4 b, and causes the refrigerant returning from the heatmedium relay unit 3 during the heating operation to flow to the suctionside of the compressor 10. The check valve 13 d is provided on arefrigerant pipe 4 between the heat medium relay unit 3 and the firstrefrigerant flow switching device 11, and allows the flow of refrigerantonly in a designated direction (the direction from the heat medium relayunit 3 to the outdoor unit 1).

The first connecting pipe 4 a connects, inside the outdoor unit 1, therefrigerant pipe 4 between the first refrigerant flow switching device11 and the check valve 13 d, and the refrigerant pipe 4 between thecheck valve 13 a and the heat medium relay unit 3.

The second connecting pipe 4 b connects, inside the outdoor unit 1, therefrigerant pipe 4 between the check valve 13 d and the heat mediumrelay unit 3, and refrigerant pipe 4 between the heat source side heatexchanger 12 and the check valve 13 a. By providing the first connectingpipe 4 a, the second connecting pipe 4 b, and the check valves 13 a to13 d, it is possible to keep the flow of refrigerant flowing into theheat medium relay unit 3 going in a fixed direction, regardless of theoperation demanded by the indoor units 2.

The two branching units 27 (branching unit 27 a, branching unit 27 b)cause inflowing refrigerant to branch. The refrigerant inflow side ofthe branching unit 27 a is connected to the refrigerant pipe 4 on whichthe check valve 13 a is provided, while one end on the refrigerantoutflow side is connected to the refrigerant pipe 4 that connects theoutdoor unit 1 and the heat medium relay unit 3, and the other end onthe refrigerant outflow side is connected to the branch pipe 4 d. Also,the refrigerant inflow side of the branching unit 27 b is connected tothe refrigerant pipe 4 that connects the heat medium relay unit 3 andthe outdoor unit 1, while one end of the refrigerant outflow side isconnected to the refrigerant pipe 4 on which the check valve 13 d isprovided and the second connecting pipe 4 b, and the other end of therefrigerant outflow side is connected to the branch pipe 4 d. Note thatthe branching units 27 may be made up of Y-junctions, T-junctions, orthe like, for example.

Liquid refrigerant or two-phase gas-liquid refrigerant flows into thebranching units 27, depending on the operation mode of theair-conditioning apparatus 100. For example, in the case of the coolingmain operation mode, two-phase gas-liquid refrigerant flows into thebranching unit 27 a, while in the case of the heating only operationmode and the heating main operation mode, two-phase gas-liquidrefrigerant flows into the branching unit 27 b. Accordingly, in order toequally distribute the two-phase gas-liquid refrigerant, the branchingunits 27 are structured so as to split the flow in a configuration statesuch that refrigerant branches into two after flowing from bottom totop. In other words, take the refrigerant inflow side of the branchingunits 27 to be the lower side (lower in the gravitational direction),and take the refrigerant outflow sides of the branching units 27 (bothsides) to be the upper side (upper in the gravitational direction). Inso doing, two-phase gas-liquid refrigerant flowing into the branchingunits 27 may be equally distributed, and it is possible to moderatereductions in the air conditioning performance of the air-conditioningapparatus 100.

The opening and closing device 24 opens and closes the flow between thebranching unit 27 a and the suction injection pipe 4 c. The opening andclosing device 24 opens in the case of injecting in the cooling onlyoperation mode and in the case of injecting in the cooling mainoperation mode, and closes in the case of not injecting. In addition,the opening and closing device 24 closes in the heating only operationmode and the heating main operation mode. The opening and closing device24 is provided on the branch pipe 4 d, with one end connected to thebranching unit 27 a, and the other end connected to the suctioninjection pipe 4 c. Note that the opening and closing device 24 may beanything capable of switching a flow open/closed, such as a solenoidvalve capable of open/close switching, an electronic expansion valvecapable of varying an aperture surface area, or the like.

The backflow prevention device 20 makes refrigerant flow from thebranching unit 27 b to the suction injection pipe 4 c in the case ofinjecting in the heating only operation mode and the case of injectingin the heating main operation mode. Note that the backflow preventiondevice 20 closes in the case of injecting in the cooling only operationmode and the case of injecting in the cooling main operation mode. Notethat although FIG. 2 illustrates the case in which the backflowprevention device 20 is a check valve as an example, a solenoid valvecapable of open/close switching, an electronic expansion valve capableof varying an aperture surface area, or the like is also acceptable.

The medium pressure detection device 32 detects the pressure ofrefrigerant flowing between the branching unit 27 b and the expansiondevice 14 a. In other words, the medium pressure detection device 32detects the pressure of medium pressure refrigerant that wasdepressurized by the expansion devices 16 of the heat medium relay unit3 and returned to the outdoor unit 1. The medium pressure detectiondevice 32 is provided between the branching unit 27 b and the expansiondevice 14 a.

The high pressure detection device 39 detects the pressure ofrefrigerant that was pressurized by the compressor 10 and reached highpressure. The high pressure detection device 39 is provided on therefrigerant pipe 4 connected on the discharge side of the compressor 10.

The medium pressure detection device 32 and the high pressure detectiondevice 39 may be pressure sensors, but may also be made up oftemperature sensors. In other words, it is also possible to enable thecontroller 50 to compute a medium pressure by computation on the basisof a detected temperature.

The discharge refrigerant temperature detection device 37 detects thetemperature of refrigerant discharged from the compressor 10, and isprovided on the refrigerant pipe 4 connected on the discharge side ofthe compressor 10.

A suction refrigerant temperature detection device 38 detects thetemperature of refrigerant flowing into the compressor 10, and isprovided on the refrigerant pipe 4 on the downstream side of theaccumulator 19.

A branch refrigerant temperature detection device 33 detects thetemperature of refrigerant flowing into the branching unit 27 a, and isprovided in the flow on the inflow side of the branching unit 27 a.

A suction pressure detection device 60 detects the pressure ofrefrigerant suctioned into the compressor 10, and is provided on therefrigerant pipe 4 on the upstream side of the accumulator 19.

A compressor shell temperature detection device 61 detects thetemperature of the shell of the compressor 10, and is provided on thebottom of the shell of the compressor 10. Note that the compressor 10provided with the compressor shell temperature detection device 61 is alow-pressure shell-structure compressor, which typically includes acompression chamber inside a hermetically sealed container (the shell),in which the inside of the hermetically sealed container is in alow-pressure refrigerant pressure environment, and that suctions andcompresses low-pressure refrigerant inside the hermetically sealedcontainer into the compression chamber. However, in Embodiment 1, thecompressor 10 is not limited to such a compressor.

The two expansion devices 14 (expansion device 14 a, expansion device 14b) function as a pressure-reducing valve or an expansion valve, droppingthe pressure to cause refrigerant to expand. The expansion device 14 ais provided on the second connecting pipe 4 b (the flow leading from thebranching unit 27 b to the heat source side heat exchanger 12 in theheating only operation mode and the heating main operation modediscussed later), and is provided on the upstream side of the checkvalve 13 c. Meanwhile, the expansion device 14 b is provided on thesuction injection pipe 4 c. Two-phase gas-liquid refrigerant flows intothe expansion device 14 a in the case of the heating only operation modeand the heating main operation mode. Meanwhile, liquid refrigerant flowsinto the expansion device 14 b during the cooling only operation mode,whereas refrigerant in a two-phase gas-liquid state flows into theexpansion device 14 b in the case of the cooling main operation mode,the heating only operation mode, and the heating main operation mode.

The expansion device 14 a may be configured as an electronic expansionvalve that is capable of varying an aperture surface area. If theexpansion device 14 a is configured with an electronic expansion valve,it is possible to control the pressure on the upstream side of theexpansion device 14 a to an arbitrary pressure. Note that the expansiondevice 14 a is not limited to an electronic expansion valve, andalthough controllability suffers slightly, compact solenoid valves orthe like may also be combined to enable selecting from multiple aperturesurface areas, or configured as a capillary tube such that a mediumpressure is formed due to refrigerant pressure loss.

Also, the expansion device 14 b likewise may be configured as anelectronic expansion valve that is capable of varying an aperturesurface area. In the case of injecting, this expansion device 14 bcontrols the aperture surface area of the expansion device 14 b suchthat the discharge refrigerant temperature of the compressor 10 detectedby the discharge refrigerant temperature detection device 37 does notbecome too high.

The suction injection pipe 4 c is a pipe that supplies liquidrefrigerant to the compressor 10. Herein, suction injection referssupplying liquid refrigerant to the refrigerant pipe 4 between thecompressor 10 and the accumulator 19, or in other words, on the suctionside of the compressor 10.

One end of the suction injection pipe 4 c is connected to the branchpipe 4 d, while the other end is connected to the refrigerant pipe 4that connects the accumulator 19 and the compressor 10. The expansiondevice 14 b is provided on the suction injection pipe 4 c.

The branch pipe 4 d is a pipe for leading refrigerant to the suctioninjection pipe 4 c in the case of injection into the compressor 10. Thebranch pipe 4 d is connected to the branching unit 27 a, the branchingunit 27 b, and the suction injection pipe 4 c. The backflow preventiondevice 20 and the opening and closing device 24 are provided on thebranch pipe 4 d.

The controller 50 is made up of a microcontroller or the like, andconducts control on the basis of detected information from variousdetection devices as well as instructions from a remote control. Besidescontrolling the actuators discussed earlier, the controller 50 isconfigured to control the driving frequency of the compressor 10, therotation speed of the air-sending device provided in the heat sourceside heat exchanger 12 (including ON/OFF), the opening and closing ofthe opening and closing device 24, the opening degree (expansion amount)of the expansion device 14, the switching of the first refrigerant flowswitching device 11, and various equipment provided in the heat mediumrelay unit 3 and the indoor units 2, and to execute the respectiveoperation modes discussed later.

During the cooling only operation mode and the cooling main operationmode, the controller 50 is able to control the flow rate of refrigerantto inject by opening the opening and closing device 24 and adjusting theopening degree of the expansion device 14 b. Also, during the heatingonly operation mode and the heating main operation mode, the controller50 is able to control the flow rate of refrigerant to inject by closingthe opening and closing device 24 and adjusting the opening degrees ofthe expansion device 14 a and the expansion device 14 b. Then, byinjecting into the compressor 10, it is possible to reduce thetemperature of refrigerant discharged from the compressor 10. Note thatspecific control operations will be described in the operationaldescription of each operation mode discussed later.

Note that in the case of injecting, control of the discharge refrigeranttemperature by the expansion device 14 b stabilizes if, for theexpansion device 14 a, the controller 50 controls the opening degree ofthe expansion device 14 a such that the medium pressure detected by themedium pressure detection device 32 becomes a fixed value (target value)during the heating only operation mode and the heating main operationmode.

More specifically, control of the discharge refrigerant temperature bythe expansion device 14 b stabilizes if the controller 50 controls theopening degree of the expansion device 14 a such that the detectedpressure of the medium pressure detection device 32 or the saturationpressure of the detected temperature of the medium pressure detectiondevice 32, or alternatively, the detected temperature of the mediumpressure detection device 32 or the saturation temperature of thedetected pressure of the medium pressure detection device 32, reaches afixed value (target value).

Also, in the case of injecting, for the expansion device 14 b thecontroller 50 may control the aperture surface area of the expansiondevice 14 b such that the discharge refrigerant temperature of thecompressor 10 detected by the discharge refrigerant temperaturedetection device 37 does not become too high.

More specifically, upon determining that the discharge refrigeranttemperature has exceeded a fixed value (such as 110 degrees C., forexample), the expansion device 14 b may be controlled to open a fixedopening degree, such as 10 pulses each, for example, or the openingdegree of the expansion device 14 b may be controlled such that thedischarge refrigerant temperature becomes a target value (100 degreesC., for example), or controlled such that the discharge refrigeranttemperature becomes less than or equal to a target value (100 degreesC., for example), or controlled such that the discharge refrigeranttemperature falls within a target range (between 90 degrees C. to 100degrees C., for example).

Furthermore, the controller 50 may also be configured to compute adischarge degree of superheat of the compressor 10 from the detectedtemperature of the discharge refrigerant temperature detection device 37and the detected pressure of the high pressure detection device 39, andcontrol the opening degree of the expansion device 14 b such that thedischarge degree of superheat becomes a target value (40 degrees C., forexample), or apply control such that the discharge degree of superheatbecomes less than or equal to a target value (40 degrees C., forexample), or apply control such that the discharge degree of superheatfalls within a target range (between 20 degrees C. and 40 degrees C.,for example).

[Indoor Units 2]

The indoor units 2 are respectively equipped with use side heatexchangers 26. The use side heat exchangers 26 are connected to heatmedium flow control devices 25 and second heat medium flow switchingdevices 23 of the heat medium relay unit 3 by the pipes 5. The use sideheat exchangers 26 exchange heat between heat medium and air suppliedfrom an air-sending device such as a fan (not illustrated), and generateheated air or cooled air to supply to the indoor space 7.

FIG. 2 illustrates a case in which four indoor units 2 are connected tothe heat medium relay unit 3 as an example, these being indicated as anindoor unit 2 a, an indoor unit 2 b, an indoor unit 2 c, and an indoorunit 2 d from the bottom of the page. Also, the use side heat exchanger26 are indicated as a use side heat exchanger 26 a, a use side heatexchanger 26 b, a use side heat exchanger 26 c, and a use side heatexchanger 26 d from the bottom of the page, in correspondence with theindoor unit 2 a to the indoor unit 2 d. Note that, similarly to FIG. 1,the number of connected indoor units 2 is not limited to the four asillustrated in FIG. 2.

[Heat Medium Relay Unit 3]

The heat medium relay unit 3 is equipped with two intermediate heatexchangers 15, two expansion devices 16, two opening and closing devices17, two second refrigerant flow switching devices 18, two pumps 21, fourfirst heat medium flow switching devices 22, four second heat mediumflow switching devices 23, and four heat medium flow control devices 25.

The two intermediate heat exchangers 15 (intermediate heat exchanger 15a, intermediate heat exchanger 15 b) function as condensers (radiators)or evaporators, exchanging heat between refrigerant and a heat medium,and transferring cooling energy or heating energy generated by theoutdoor unit 1 and stored in the refrigerant to the heat medium. Theintermediate heat exchanger 15 a is provided between the expansiondevice 16 a and the second refrigerant flow switching device 18 a on therefrigerant circuit A, serving to cool the heat medium during thecooling only operation mode, heat the heat medium during the heatingonly operation mode, and cool the heat medium during the cooling andheating mixed operation mode. Meanwhile, the intermediate heat exchanger15 b is provided between the expansion device 16 b and the secondrefrigerant flow switching device 18 b on the refrigerant circuit A,serving to cool the heat medium during the cooling only operation mode,heat the heat medium during the heating only operation mode, and heatthe heat medium during the cooling and heating mixed operation mode.

The two expansion devices 16 (expansion device 16 a, expansion device 16b) have the function of a pressure-reducing valve or an expansion valve,dropping the pressure to cause refrigerant to expand. The expansiondevice 16 a is provided on the upstream side of the intermediate heatexchanger 15 a with respect to the flow of refrigerant during thecooling operation. The expansion device 16 b is provided on the upstreamside of the intermediate heat exchanger 15 b with respect to the flow ofrefrigerant during the cooling operation. The two expansion devices 16may have variably controllable opening degrees, and may be configured asan electronic expansion valve or the like, for example.

The two opening and closing devices 17 (opening and closing device 17 a,opening and closing device 17 b) are made up of a two-way valve or thelike, and opening and closing the refrigerant pipes 4. The opening andclosing device 17 a is provided in a refrigerant pipe 4 at therefrigerant inlet side. The opening and closing device 17 b is providedin a pipe connecting refrigerant pipes 4 on the refrigerant inlet sideand outlet side. The two second refrigerant flow switching devices 18(second refrigerant flow switching device 18 a, second refrigerant flowswitching device 18 b) are made up of a four-way valve or the like,switching the flow of refrigerant according to the operation mode. Thesecond refrigerant flow switching device 18 a is provided on thedownstream side of the intermediate heat exchanger 15 a with respect tothe flow of refrigerant during the cooling operation. The secondrefrigerant flow switching device 18 b is provided on the downstreamside of the intermediate heat exchanger 15 b with respect to the flow ofrefrigerant during the cooling only operation.

The two pumps 21 (pump 21 a, pump 21 b) circulate the heat mediumconducted through the pipes 5. The pump 21 a is provided on a pipe 5between the intermediate heat exchanger 15 a and the second heat mediumflow switching devices 23. The pump 21 b is provided on a pipe 5 betweenthe intermediate heat exchanger 15 b and the second heat medium flowswitching devices 23. The two pumps 21 may be configured asvariable-capacity pumps or the like, for example.

The four first heat medium flow switching devices 22 (first heat mediumflow switching device 22 a to first heat medium flow switching device 22d) are made up of a three-way valve or the like, and switch the flow ofthe heat medium. The number of first heat medium flow switching devices22 provided corresponds to the number of installed indoor units 2(herein, four). In the first heat medium flow switching devices 22, oneof the three ways is connected to the intermediate heat exchanger 15 a,one of the three ways is connected to the intermediate heat exchanger 15b, and one of the three ways is connected to the heat medium flowcontrol devices 25, and are provided on the outlet side of the heatmedium flows of the use side heat exchangers 26. Note that the firstheat medium flow switching devices 22 are indicated as a first heatmedium flow switching device 22 a, a first heat medium flow switchingdevice 22 b, a first heat medium flow switching device 22 c, and a firstheat medium flow switching device 22 d from the bottom of the page, incorrespondence with the indoor units 2.

The four second heat medium flow switching devices 23 (second heatmedium flow switching device 23 a to second heat medium flow switchingdevice 23 d) are made up of a three-way valve or the like, and switchthe flow of the heat medium. The number of second heat medium flowswitching devices 23 provided corresponds to the number of installedindoor units 2 (herein, four). In the second heat medium flow switchingdevices 23, one of the three ways is connected to the intermediate heatexchanger 15 a, one of the three ways is connected to the intermediateheat exchanger 15 b, and one of the three ways is connected to the useside heat exchangers 26, and are provided on the inlet side of the heatmedium flows of the use side heat exchangers 26. Note that the secondheat medium flow switching devices 23 are indicated as a second heatmedium flow switching device 23 a, a second heat medium flow switchingdevice 23 b, a second heat medium flow switching device 23 c, and asecond heat medium flow switching device 23 d from the bottom of thepage, in correspondence with the indoor units 2.

The four heat medium flow control devices 25 (heat medium flow controldevice 25 a to heat medium flow control device 25 d) are made up of atwo-way valve or the like with a controllable opening surface area, andcontrol the flow rate flowing through the pipes 5. The number of heatmedium flow control devices 25 provided corresponds to the number ofinstalled indoor units 2 (herein, four). The heat medium flow controldevices 25 are connected to the use side heat exchangers 26 on one endand to the first heat medium flow switching devices 22 on the other end,and are provided on the outlet side of the heat medium flow channel ofthe use side heat exchangers 26. Note that the heat medium flow controldevices 25 are indicated as a heat medium flow control device 25 a, aheat medium flow control device 25 b, a heat medium flow control device25 c, and a heat medium flow control device 25 d from the bottom of thepage, in correspondence with the indoor units 2. Also, the heat mediumflow control devices 25 may be provided on the inlet side of the heatmedium flow channels of the use side heat exchangers 26.

The heat medium relay unit 3 is further provided with various detectiondevices (two first temperature sensors 31, four second temperaturesensors 34, four third temperature sensors 35, and one pressure sensor36). Information detected by these detection devices (temperatureinformation, pressure information) is sent to a controller (notillustrated) that centrally controls operation of the air-conditioningapparatus 100, and is used to control the driving frequency of thecompressor 10, the rotation speed of the air-sending device that is notillustrated, the switching of the first refrigerant flow switchingdevice 11, the driving frequency of the pumps 21, the switching of thesecond refrigerant flow switching devices 18, the switching of the flowof the heat medium, and the like.

The two first temperature sensors 31 (first temperature sensor 31 a,first temperature sensor 31 b) detect the temperature of the heat mediumflowing out from the intermediate heat exchangers 15, or in other words,the heat medium at the outlets of the intermediate heat exchangers 15,and may be made up of thermistors or the like, for example. The firsttemperature sensor 31 a is provided in the pipe 5 on the inlet side ofthe pump 21 a. The first temperature sensor 31 b is provided in the pipe5 on the inlet side of the pump 21 b.

The four second temperature sensors 34 (second temperature sensor 34 ato second temperature sensor 34 d) are provided between the first heatmedium flow switching devices 22 and the heat medium flow controldevices 25, detect the temperature of the heat medium flowing out fromthe use side heat exchangers 26, and may be made up of thermistors orthe like. The number of second temperature sensors 34 providedcorresponds to the number of installed indoor units 2 (herein, four).Note that the second temperature sensors 34 are indicated as a secondtemperature sensor 34 a, a second temperature sensor 34 b, a secondtemperature sensor 34 c, and a second temperature sensor 34 d from thebottom of the page, in correspondence with the indoor units 2.

The four third temperature sensors 35 (third temperature sensor 35 a tothird temperature sensor 35 d) are provided on the refrigerant inletside or outlet side of the intermediate heat exchangers 15, detect thetemperature of refrigerant flowing into the intermediate heat exchangers15 or the temperature of refrigerant flowing out from the intermediateheat exchangers 15, and may be made up of thermistors or the like. Thethird temperature sensor 35 a is provided between the intermediate heatexchanger 15 a and the second refrigerant flow switching device 18 a.The third temperature sensor 35 b is provided between the intermediateheat exchanger 15 a and the expansion device 16 a. The third temperaturesensor 35 c is provided between the intermediate heat exchanger 15 b andthe second refrigerant flow switching device 18 b. The third temperaturesensor 35 d is provided between the intermediate heat exchanger 15 b andthe expansion device 16 b.

The pressure sensor 36 is provided between the intermediate heatexchanger 15 b and the expansion device 16 b, similarly to theinstallation position of the third temperature sensor 35 d, and detectsthe pressure of refrigerant flowing between the intermediate heatexchanger 15 b and the expansion device 16 b.

Additionally, a controller provided in the heat medium relay unit 3 (notillustrated) is made up of a microcontroller or the like, and on thebasis of detected information from various detection devices as well asinstructions from a remote control, controls the driving of the pumps21, the opening degree of the expansion devices 16, the opening degreeof the opening and closing devices 17, the switching of the secondrefrigerant flow switching devices 18, the switching of the first heatmedium flow switching devices 22, the switching of the second heatmedium flow switching devices 23, the opening degree of the heat mediumflow control devices 25, and the like, and execute the respectiveoperation modes discussed later. Note that a controller that controlsthe operations of both the outdoor unit 1 and the heat medium relay unit3 may also be provided in only one of the outdoor unit 1 and the heatmedium relay unit 3.

[Refrigerant Pipes 4]

The outdoor unit 1 and the heat medium relay unit 3 are connected byrefrigerant pipes 4, and refrigerant flows through the refrigerant pipes4.

[Pipes 5]

The heat medium relay unit 3 and the indoor units 2 are connected by(heat medium) pipes 5, and a heat medium such as water or antifreezeflows through the pipes 5.

The pipes 5 that conduct the heat medium are made up of those connectedto the intermediate heat exchanger 15 a, and those connected to theintermediate heat exchanger 15 b. The pipes 5 are branched according tothe number of indoor units 2 connected to the heat medium relay unit 3(herein, a four-way branch each). Additionally, the pipes 5 areconnected by the first heat medium flow switching devices 22 and thesecond heat medium flow switching devices 23. By controlling the firstheat medium flow switching devices 22 and the second heat medium flowswitching devices 23, it is decided whether to circulate a heat mediumfrom the intermediate heat exchanger 15 a into the use side heatexchangers 26, or circulate the heat medium from the intermediate heatexchanger 15 b into the use side heat exchangers 26.

In addition, in the air-conditioning apparatus 100, the compressor 10,the first refrigerant flow switching device 11, the heat source sideheat exchanger 12, the opening and closing devices 17, the secondrefrigerant flow switching devices 18, the refrigerant flow of theintermediate heat exchanger 15 a, the expansion devices 16, and theaccumulator 19 are connected by the refrigerant pipes 4 to constitute arefrigerant circuit A. Meanwhile, the heat medium flow of theintermediate heat exchanger 15 a, the pumps 21, the first heat mediumflow switching devices 22, the heat medium flow control devices 25, theuse side heat exchangers 26, and the second heat medium flow switchingdevices 23 are connected by the pipes 5 to constitute a heat mediumcircuit B. In other words, multiple use side heat exchangers 26 areconnected in parallel to each of the intermediate heat exchangers 15,making the heat medium circuit B a multi-branch circuit.

Thus, in the air-conditioning apparatus 100, the outdoor unit 1 and theheat medium relay unit 3 are connected via the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b provided in theheat medium relay unit 3, while the heat medium relay unit 3 and theindoor units 2 are also connected via the intermediate heat exchanger 15a and the intermediate heat exchanger 15 b. In other words, in theair-conditioning apparatus 100, heat is exchanged between therefrigerant circulating through the refrigerant circuit A and the heatmedium circulating through the heat medium circuit B by the intermediateheat exchanger 15 a and the intermediate heat exchanger 15 b.

Next, the respective operation modes executed by the air-conditioningapparatus 100 will be described. The air-conditioning apparatus 100 iscapable of the cooling operation or the heating operation with eachindoor unit 2, on the basis of instructions from each indoor unit 2. Inother words, the air-conditioning apparatus 100 is configured such thatall of the indoor units 2 may operate identically, but also such thateach of the indoor units 2 may operate differently.

The operation modes executed by the air-conditioning apparatus 100include a cooling only operation mode in which all indoor units 2 beingdriven execute the cooling operation, a heating only operation mode inwhich all indoor units 2 being driven execute the heating operation, acooling main operation mode in which the cooling load is larger, and aheating main operation mode in which the heating load is larger.Hereinafter, the respective operation modes will be described togetherwith the flows of refrigerant and a heat medium.

[Cooling Only Operation Mode]

FIG. 3 is a diagram explaining the flow of refrigerant and heat mediumduring the cooling only operation of the air-conditioning apparatus 100illustrated in FIG. 2. The cooling only operation mode will be describedwith FIG. 3, taking as an example the case where a cooling load isgenerated by only the use side heat exchanger 26 a and the use side heatexchanger 26 b. Note that in FIG. 3, pipes indicated in bold representpipes carrying refrigerant (refrigerant and a heat medium). Also, inFIG. 3, solid arrows indicate the direction of refrigerant flow, whiledashed arrows represent the direction of heat medium flow.

In the case of the cooling only operation mode illustrated in FIG. 3, inthe outdoor unit 1, the first refrigerant flow switching device 11switches such that refrigerant discharged from the compressor 10 flowsinto the heat source side heat exchanger 12. In the heat medium relayunit 3, the pump 21 a and the pump 21 b are driven, the heat medium flowcontrol device 25 a and the heat medium flow control device 25 b arefully opened, and the heat medium flow control device 25 c and the heatmedium flow control device 25 d are fully closed, causing heat medium tocirculate between each of the intermediate heat exchanger 15 a and theintermediate heat exchanger 15 b, and the use side heat exchanger 26 aand the use side heat exchanger 26 b, respectively.

First, the flow of refrigerant in the refrigerant circuit A will bedescribed.

Low temperature and low pressure refrigerant is compressed by thecompressor 10 to become high temperature and high pressure gasrefrigerant, and is discharged. The high temperature and high pressuregas refrigerant discharged from the compressor 10 flows into the heatsource side heat exchanger 12 via the first refrigerant flow switchingdevice 11. Then, the refrigerant condenses and liquefies whiletransferring heat to the outside air in the heat source side heatexchanger 12, and becomes high pressure liquid refrigerant. The highpressure liquid refrigerant flowing out from the heat source side heatexchanger 12 passes through the check valve 13 a, flows out from theoutdoor unit 1 via the branching unit 27 a, and goes through therefrigerant pipes 4 to flow into the heat medium relay unit 3. Afterpassing through the opening and closing device 17 a, the high pressuretwo-phase gas-liquid refrigerant flowing into the heat medium relay unit3 is branched and expanded by the expansion device 16 a and theexpansion device 16 b to become a low temperature and low pressuretwo-phase refrigerant.

The two-phase refrigerant respectively flows into the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b which act asevaporators, and evaporates to become low temperature and low pressuregas refrigerant while cooling the heat medium by taking away heat fromthe heat medium circulating through the heat medium circuit B. The gasrefrigerant flowing out of the intermediate heat exchanger 15 a and theintermediate heat exchanger 15 b flows out from the heat medium relayunit 3 via the second refrigerant flow switching device 18 a and thesecond refrigerant flow switching device 18 b, and passes through therefrigerant pipes 4 to once again flow into the outdoor unit 1. Therefrigerant flowing into the outdoor unit 1 passes through the checkvalve 13 d via the branching unit 27 b, and is once again suctioned intothe compressor 10 via the first refrigerant flow switching device 11 andthe accumulator 19.

At this point, the opening degree of the expansion device 16 a iscontrolled such that the superheat (degree of superheat) obtained as thedifference between the temperature detected by the third temperaturesensor 35 a and the temperature detected by the third temperature sensor35 b becomes constant. Similarly, the opening degree of the expansiondevice 16 b is controlled such that the superheat obtained as thedifference between the temperature detected by the third temperaturesensor 35 c and the temperature detected by the third temperature sensor35 d becomes constant. Also, the opening and closing device 17 a opens,while the opening and closing device 17 b closes.

[Cooling Only Operation Mode p-h Chart]

FIG. 4 is a pressure-enthalpy chart (p-h chart) during the cooling onlyoperation illustrated in FIG. 3. Injection operations in this mode willbe described using FIG. 3 and the p-h chart in FIG. 4.

Refrigerant suctioned into the compressor 10 and compressed by thecompressor 10 is condensed in the heat source side heat exchanger 12 tobecome high pressure liquid refrigerant (point J in FIG. 4). This highpressure liquid refrigerant reaches the branching unit 27 a via thecheck valve 13 a.

In the case of conducting injection, the opening and closing device 24opens, and part of the high pressure liquid refrigerant branched at thebranching unit 27 a is made to flow into the suction injection pipe 4 cvia the opening and closing device 24 and the branch pipe 4 d. The highpressure liquid refrigerant flowing into the suction injection pipe 4 cis depressurized by the expansion device 14 b to become a lowtemperature and low pressure two-phase gas-liquid refrigerant (point Kin FIG. 4), and flows into a refrigerant pipe joining the compressor 10and the accumulator 19.

Meanwhile, the remaining high pressure liquid refrigerant branched atthe branching unit 27 a flows into the heat medium relay unit 3, isdepressurized by the expansion devices 16 to become a low pressuretwo-phase gas-liquid refrigerant, and flows into the intermediate heatexchangers 15 which function as evaporators, becoming a low temperatureand low pressure gas refrigerant. After that, the low temperature andlow pressure gas refrigerant flows into the outdoor unit 1, and flowsinto the accumulator 19.

The low temperature and low pressure two-phase gas-liquid refrigerantflowing out from the suction injection pipe 4 c converges with the lowtemperature and low pressure gas refrigerant flowing out from theaccumulator 19 at a refrigerant pipe 4 connected on the suction side ofthe compressor 10 (point H in FIG. 4), and is suctioned into thecompressor 10. The low temperature and low pressure two-phase gas-liquidrefrigerant suctioned into the compressor 10 is heated and evaporated bythe hermetically sealed container and the motor of the compressor 10,becomes a low temperature and low pressure gas refrigerant at a lowertemperature than in the case of not conducting injection, is suctionedinto the compression chamber of the compressor 10, and is once againdischarged from the compressor 10 (point I in FIG. 4).

Note that in the case of not conducting injection, the opening andclosing device 24 closes, and the high pressure liquid refrigerantbranched at the branching unit 27 a is depressurized by the expansiondevices 16 to become a low pressure two-phase gas-liquid refrigerant,flows into the intermediate heat exchangers 15, which function asevaporators, to become a low temperature and low pressure gasrefrigerant, and is suctioned into the compressor 10 via the accumulator19 (point F in FIG. 4). This low temperature and low pressure gasrefrigerant is heated and evaporated by the hermetically sealedcontainer and the motor of the compressor 10, becomes a low temperatureand low pressure gas refrigerant at a higher temperature than in thecase of conducting injection, is suctioned into the compression chamberof the compressor 10, and is once again discharged from the compressor10 (point G in FIG. 4).

In addition, the temperature of refrigerant discharged from thecompressor 10 in the case of conducting injection (point I in FIG. 4)lowers with respect to the temperature of refrigerant discharged fromthe compressor 10 in the case of not conducting injection (point G inFIG. 4). In this way, even if the air-conditioning apparatus 100 employsa refrigerant whose discharge refrigerant temperature from thecompressor 10 reaches a high temperature (such as R32, for example), itis possible to lower the discharge refrigerant temperature of thecompressor 10, and improve the stability of the operation of theair-conditioning apparatus 100.

Note that the refrigerant in the flow proceeding from the opening andclosing device 24 in the branch pipe 4 d to the backflow preventiondevice 20 is high pressure refrigerant, whereas the refrigerant whichreturns to the outdoor unit 1 from the heat medium relay unit 3 via therefrigerant pipes 4 and reaches the branching unit 27 b is low pressurerefrigerant. Due to the action of the backflow prevention device 20, thehigh pressure refrigerant in the branch pipe 4 d is prevented frommixing with the low pressure refrigerant in the branching unit 27 b.Since refrigerant does not flow through the expansion device 14 a, anarbitrary opening degree may be set. The expansion device 14 b maycontrol the opening degree (expansion amount) such that the dischargerefrigerant temperature of the compressor 10 detected by the dischargerefrigerant temperature detection device 37 does not become too high.

Next, the flow of heat medium in the heat medium circuit B will bedescribed.

In the cooling only operation mode, the cooling energy of therefrigerant is transferred to the heat medium in both the intermediateheat exchanger 15 a and the intermediate heat exchanger 15 b, and thecooled heat medium is made to flow inside the pipes 5 by the pump 21 aand the pump 21 b. The outflowing heat medium pressurized by the pump 21a and the pump 21 b flows into the use side heat exchanger 26 a and theuse side heat exchanger 26 b via the second heat medium flow switchingdevice 23 a and the second heat medium flow switching device 23 b. Then,the heat medium takes away heat from the indoor air at the use side heatexchanger 26 a and the use side heat exchanger 26 b, thereby cooling theindoor space 7.

Subsequently, the heat medium flows out from the use side heat exchanger26 a and the use side heat exchanger 26 b, and flows into the heatmedium flow control device 25 a and the heat medium flow control device25 b. At this point, the heat medium is made to flow into the use sideheat exchanger 26 a and the use side heat exchanger 26 b at a flow ratecontrolled by the action of the heat medium flow control device 25 a andthe heat medium flow control device 25 b, this flow rate being the flowrate of heat medium necessary to cover the air conditioning loadrequired indoors. The heat medium flowing out from the heat medium flowcontrol device 25 a and the heat medium flow control device 25 b passesthrough the first heat medium flow switching device 22 a and the firstheat medium flow switching device 22 b, flows into the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b, and is onceagain suctioned into the pump 21 a and the pump 21 b.

Note that inside the pipes 5 of the use side heat exchangers 26, theheat medium flows in the direction going from the second heat mediumflow switching devices 23 to the first heat medium flow switchingdevices 22 via the heat medium flow control devices 25. In addition, theair conditioning load required in the indoor space 7 may be covered byapplying control to keep the difference between the temperature detectedby the first temperature sensor 31 a or the temperature detected by thefirst temperature sensor 31 b and the temperature detected by the secondtemperature sensors 34 at a target value. The temperature of either thefirst temperature sensor 31 a or the first temperature sensor 31 b maybe used as the outlet temperature of the intermediate heat exchangers15, or their average temperature may be used. At this point, the firstheat medium flow switching devices 22 and the second heat medium flowswitching devices 23 are set to intermediate opening degrees to maintainflows flowing into both the intermediate heat exchanger 15 a and theintermediate heat exchanger 15 b.

[Heating Only Operation Mode]

FIG. 5 is a diagram explaining the flow of refrigerant and heat mediumduring the heating only operation of the air-conditioning apparatus 100illustrated in FIG. 2. The heating only operation mode will be describedwith FIG. 5, taking as an example the case where a heating load isgenerated by only the use side heat exchanger 26 a and the use side heatexchanger 26 b. Note that in FIG. 5, pipes indicated in bold representpipes carrying refrigerant (refrigerant and a heat medium). Also, inFIG. 5, solid arrows indicate the direction of refrigerant flow, whiledashed arrows represent the direction of heat medium flow.

In the case of the heating only operation mode illustrated in FIG. 5, inthe outdoor unit 1, the first refrigerant flow switching device 11switches such that refrigerant discharged from the compressor 10 flowsinto the heat medium relay unit 3 without passing through the heatsource side heat exchanger 12. In the heat medium relay unit 3, the pump21 a and the pump 21 b are driven, the heat medium flow control device25 a and the heat medium flow control device 25 b are fully opened, andthe heat medium flow control device 25 c and the heat medium flowcontrol device 25 d are fully closed, causing heat medium to circulatebetween each of the intermediate heat exchanger 15 a and theintermediate heat exchanger 15 b, and the use side heat exchanger 26 aand the use side heat exchanger 26 b, respectively.

First, the flow of refrigerant in the refrigerant circuit A will bedescribed.

Low temperature and low pressure refrigerant is compressed by thecompressor 10 to become high temperature and high pressure gasrefrigerant, and is discharged. The high temperature and high pressuregas refrigerant discharged from the compressor 10 goes through the firstrefrigerant flow switching device 11, is conducted through the firstconnecting pipe 4 a, passes through the check valve 13 b and thebranching unit 27 a, and flows out from the outdoor unit 1. The hightemperature and high pressure gas refrigerant flowing out of the outdoorunit 1 flows into the heat medium relay unit 3 via the refrigerant pipes4. The high temperature and high pressure gas refrigerant flowing intothe heat medium relay unit 3 is branched, goes through the secondrefrigerant flow switching device 18 a and the second refrigerant flowswitching device 18 b, and respectively flows into the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b.

The high temperature and high pressure gas refrigerant flowing into theintermediate heat exchanger 15 a and the intermediate heat exchanger 15b condenses and liquefies to become high pressure liquid refrigerantwhile transferring heat to the heat medium circulating through the heatmedium circuit B. The liquid refrigerant flowing out of the intermediateheat exchanger 15 a and the intermediate heat exchanger 15 b is expandedby the expansion device 16 a and the expansion device 16 b to become amedium temperature and medium pressure two-phase refrigerant. Thistwo-phase refrigerant goes through the opening and closing device 17 b,flows out from the heat medium relay unit 3, goes through therefrigerant pipes 4, and once again flows into the outdoor unit 1. Therefrigerant flowing into the outdoor unit 1 flows into the secondconnecting pipe 4 b via the branching unit 27 b, goes through theexpansion device 14 a, is constricted by the expansion device 14 a tobecome low temperature and low pressure two-phase refrigerant, passesthrough the check valve 13 c, and flows into the heat source side heatexchanger 12 which acts as an evaporator.

Then, the refrigerant flowing into the heat source side heat exchanger12 takes away heat from the outside air at the heat source side heatexchanger 12, and becomes a low temperature and low pressure gasrefrigerant. The low temperature and low pressure gas refrigerantflowing out of the heat source side heat exchanger 12 is once againsuctioned into the compressor 10 via the first refrigerant flowswitching device 11 and the accumulator 19.

At this point, the opening degree of the expansion device 16 a iscontrolled such that the subcooling (degree of cooling) obtained as thedifference between the temperature detected by the third temperaturesensor 35 b and a value obtained by converting the pressure detected bythe pressure sensor 36 into a saturation temperature becomes constant.Similarly, the opening degree of the expansion device 16 b is controlledsuch that the subcooling obtained as the difference between thetemperature detected by the third temperature sensor 35 d and a valueobtained by converting the pressure detected by the pressure sensor 36into a saturation temperature becomes constant. Also, the opening andclosing device 17 a closes, while the opening and closing device 17 bopens. Note that in the case where the temperature at an intermediateposition between the intermediate heat exchangers 15 can be measured,the temperature at that intermediate position may be used instead of thepressure sensor 36, making it possible to configure the system at lowercost.

[Heating Only Operation Mode p-h Chart]

FIG. 6 is a p-h chart during the heating only operation illustrated inFIG. 5. Injection operations in this mode will be described using FIG. 5and the p-h chart in FIG. 6.

Refrigerant suctioned into the compressor 10 and compressed by thecompressor 10 flows out of the outdoor unit 1 and is condensed by theintermediate heat exchangers 15 of the heat medium relay unit 3 to reachmedium temperature, is depressurized by the expansion devices 16 toreach medium pressure (point J in FIG. 6), and flows from the heatmedium relay unit 3 into the outdoor unit 1 via the refrigerant pipes 4.The medium temperature and medium pressure two-phase refrigerant flowinginto the outdoor unit 1 reaches the branching unit 27 b.

In the case of conducting injection, the expansion device 14 b is openedto a predetermined opening degree, and part of the medium temperatureand medium pressure refrigerant branched at the branching unit 27 b ismade to flow into the suction injection pipe 4 c via the branch pipe 4d. The medium temperature and medium pressure refrigerant flowing intothe suction injection pipe 4 c is depressurized by the expansion device14 b to become a low temperature and low pressure two-phase gas-liquidrefrigerant (point K in FIG. 6), and flows into a refrigerant pipejoining the compressor 10 and the accumulator 19.

Meanwhile, the remaining medium temperature and medium pressurerefrigerant branched at the branching unit 27 b is depressurized by theexpansion device 14 a to become a low pressure two-phase gas-liquidrefrigerant, and flows into the heat source side heat exchanger 12 whichacts as an evaporator, becoming a low temperature and low pressure gasrefrigerant. After that, the low temperature and low pressure gasrefrigerant flows into the accumulator 19.

The low temperature and low pressure two-phase gas-liquid refrigerantflowing out from the suction injection pipe 4 c converges with the lowtemperature and low pressure gas refrigerant flowing out from theaccumulator 19 at a refrigerant pipe 4 connected on the suction side ofthe compressor 10 (point H in FIG. 6), and is suctioned into thecompressor 10. The low temperature and low pressure two-phase gas-liquidrefrigerant suctioned into the compressor 10 is heated and evaporated bythe hermetically sealed container and the motor of the compressor 10,becomes a low temperature and low pressure gas refrigerant at a lowertemperature than in the case of not conducting injection, is suctionedinto the compression chamber of the compressor 10, and is once againdischarged from the compressor 10 (point I in FIG. 6).

Note that in the case of not conducting injection, the expansion device14 b closes, and the medium temperature and medium pressure two-phasegas-liquid refrigerant that passed through the branching unit 27 b isdepressurized by the expansion device 14 a to become a low pressuretwo-phase gas-liquid refrigerant, flows into the heat source side heatexchanger 12, which functions as an evaporator, to become a lowtemperature and low pressure gas refrigerant, and is suctioned into thecompressor 10 via the accumulator 19 (point F in FIG. 6). This lowtemperature and low pressure gas refrigerant is heated and evaporated bythe hermetically sealed container and the motor of the compressor 10,becomes a low temperature and low pressure gas refrigerant at a highertemperature than in the case of conducting injection, is suctioned intothe compression chamber of the compressor 10, and is once againdischarged from the compressor 10 (point G in FIG. 6).

In addition, the temperature of refrigerant discharged from thecompressor 10 in the case of conducting injection (point I in FIG. 6)lowers with respect to the temperature of refrigerant discharged fromthe compressor 10 in the case of not conducting injection (point G inFIG. 6). In this way, even if the air-conditioning apparatus 100 employsa refrigerant whose discharge refrigerant temperature from thecompressor 10 reaches a high temperature (such as R32, for example), itis possible to lower the discharge refrigerant temperature of thecompressor 10, and improve the stability of the operation of theair-conditioning apparatus 100.

Note that the opening and closing device 24 closes, preventing therefrigerant in a high pressure state from the branching unit 27 a frommixing with the refrigerant in a medium pressure state coming via thebackflow prevention device 20. Also, if the expansion device 14 aapplies control such that the medium pressure detected by the mediumpressure detection device 32 becomes a constant value, control of thedischarge refrigerant temperature from the expansion device 14 bstabilizes. Furthermore, the opening degree (expansion amount) of theexpansion device 14 b is controlled such that the discharge refrigeranttemperature of the compressor 10 detected by the discharge refrigeranttemperature detection device 37 does not become too high.

Also, in the heating only operation mode, since the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b are both heatingthe heat medium, control may also be applied to raise the pressure(medium pressure) of the refrigerant on the upstream side of theexpansion device 14 a insofar as the pressure is within a range enablingthe expansion device 16 a and the expansion device 16 b to controlsubcooling. If control is applied to raise the medium pressure, thedifferential pressure between the inside of the compression chamber andthe pressure can be increased, and thus the quantity of refrigerant toinject on the suction side of the compression chamber can be increased,and it is possible to supply the compressor 10 with an injection flowrate sufficient to lower the discharge refrigerant temperature, even incases where the outside air temperature is low.

Next, the flow of heat medium in the heat medium circuit B will bedescribed.

In the heating only operation mode, the heating energy of therefrigerant is transferred to the heat medium in both the intermediateheat exchanger 15 a and the intermediate heat exchanger 15 b, and theheated heat medium is made to flow inside the pipes 5 by the pump 21 aand the pump 21 b. The outflowing heat medium pressurized by the pump 21a and the pump 21 b flows into the use side heat exchanger 26 a and theuse side heat exchanger 26 b via the second heat medium flow switchingdevice 23 a and the second heat medium flow switching device 23 b. Then,the heat medium transfers heat to the indoor air at the use side heatexchanger 26 a and the use side heat exchanger 26 b, thereby heating theindoor space 7.

Subsequently, the heat medium flows out from the use side heat exchanger26 a and the use side heat exchanger 26 b, and flows into the heatmedium flow control device 25 a and the heat medium flow control device25 b. At this point, the heat medium is made to flow into the use sideheat exchanger 26 a and the use side heat exchanger 26 b at a flow ratecontrolled by the action of the heat medium flow control device 25 a andthe heat medium flow control device 25 b, this flow rate being the flowrate of heat medium necessary to cover the air conditioning loadrequired indoors. The heat medium flowing out from the heat medium flowcontrol device 25 a and the heat medium flow control device 25 b passesthrough the first heat medium flow switching device 22 a and the firstheat medium flow switching device 22 b, flows into the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b, and is onceagain suctioned into the pump 21 a and the pump 21 b.

Note that inside the pipes 5 of the use side heat exchangers 26, theheat medium flows in the direction going from the second heat mediumflow switching devices 23 to the first heat medium flow switchingdevices 22 via the heat medium flow control devices 25. In addition, theair conditioning load required in the indoor space 7 may be covered byapplying control to keep the difference between the temperature detectedby the first temperature sensor 31 a or the temperature detected by thefirst temperature sensor 31 b and the temperature detected by the secondtemperature sensors 34 at a target value. The temperature of either thefirst temperature sensor 31 a or the first temperature sensor 31 b maybe used as the outlet temperature of the intermediate heat exchangers15, or their average temperature may be used.

At this point, the first heat medium flow switching devices 22 and thesecond heat medium flow switching devices 23 are set to intermediateopening degrees to maintain flows flowing into both the intermediateheat exchanger 15 a and the intermediate heat exchanger 15 b. Also,although the use side heat exchanger 26 a should ideally apply controlaccording to the temperature difference between the inlet and theoutlet, the heat medium temperature on the inlet side of the use sideheat exchangers 26 is nearly the same temperature as the temperaturedetected by the first temperature sensor 31 b, and thus using the firsttemperature sensor 31 b enables a reduction in the number of temperaturesensors, making it possible to configure the system at lower cost.

[Cooling Main Operation Mode]

FIG. 7 is a diagram explaining the flow of refrigerant and heat mediumduring cooling main operation of the air-conditioning apparatus 100illustrated in FIG. 2. The cooling main operation mode will be describedwith FIG. 7, taking as an example the case where a cooling load isgenerated by the use side heat exchanger 26 a, and a heating load isgenerated by the use side heat exchanger 26 b. Note that in FIG. 7,pipes indicated in bold represent pipes circulating refrigerant(refrigerant and a heat medium). Also, in FIG. 7, solid arrows indicatethe direction of refrigerant flow, while dashed arrows represent thedirection of heat medium flow.

In the case of the cooling main operation mode illustrated in FIG. 7, inthe outdoor unit 1, the first refrigerant flow switching device 11switches such that refrigerant discharged from the compressor 10 flowsinto the heat source side heat exchanger 12. In the heat medium relayunit 3, the pump 21 a and the pump 21 b are driven, the heat medium flowcontrol device 25 a and the heat medium flow control device 25 b open,and the heat medium flow control device 25 c and the heat medium flowcontrol device 25 d fully close, causing heat medium to respectivelycirculate between the intermediate heat exchanger 15 a and the use sideheat exchanger 26 a, and between the intermediate heat exchanger 15 band the use side heat exchanger 26 b.

First, the flow of refrigerant in the refrigerant circuit A will bedescribed.

Low temperature and low pressure refrigerant is compressed by thecompressor 10 to become high temperature and high pressure gasrefrigerant, and is discharged. The high temperature and high pressuregas refrigerant discharged from the compressor 10 flows into the heatsource side heat exchanger 12 via the first refrigerant flow switchingdevice 11. The refrigerant then condenses to become two-phaserefrigerant while transferring heat to the outside air in the heatsource side heat exchanger 12. The two-phase refrigerant flowing outfrom the heat source side heat exchanger 12 passes through the checkvalve 13 a, flows out from the outdoor unit 1 via the branching unit 27a, and goes through the refrigerant pipes 4 to flow into the heat mediumrelay unit 3. The two-phase refrigerant flowing into the heat mediumrelay unit 3 goes through the second refrigerant flow switching device18 b, and flows into the intermediate heat exchanger 15 b which acts asa condenser.

The two-phase refrigerant flowing into the intermediate heat exchanger15 b condenses and liquefies to become liquid refrigerant whiletransferring heat to the heat medium circulating through the heat mediumcircuit B. The liquid refrigerant flowing out of the intermediate heatexchanger 15 b is expanded by the expansion device 16 b to become lowpressure two-phase refrigerant. This low pressure two-phase refrigerantflows via the expansion device 16 a into the intermediate heat exchanger15 a, which acts as an evaporator. The low pressure two-phaserefrigerant flowing into the intermediate heat exchanger 15 a takes awayheat from the heat medium circulating through the heat medium circuit B,thus becoming low pressure gas refrigerant while cooling the heatmedium. This gas refrigerant flows out of the intermediate heatexchanger 15 a, flows out of the heat medium relay unit 3 via the secondrefrigerant flow switching device 18 a, and once again flows into theoutdoor unit 1 via the refrigerant pipes 4. The refrigerant flowing intothe outdoor unit 1 passes through the check valve 13 d via the branchingunit 27 b, and is once again suctioned into the compressor 10 via thefirst refrigerant flow switching device 11 and the accumulator 19.

At this point, the opening degree of the expansion device 16 b iscontrolled such that the superheat obtained as the difference betweenthe temperature detected by the third temperature sensor 35 a and thetemperature detected by the third temperature sensor 35 b becomesconstant. Also, the expansion device 16 a fully opens, while the openingand closing devices 17 a and 17 b close. Note that the opening degree ofthe expansion device 16 b may also be controlled such that thesubcooling obtained as the difference between the temperature detectedby the third temperature sensor 35 d and a value obtained by convertingthe pressure detected by the pressure sensor 36 into a saturationtemperature becomes constant. Also, the expansion device 16 b may fullyopen, and the superheat or subcooling may be controlled with theexpansion device 16 a.

[Cooling Main Operation Mode p-h Chart]

FIG. 8 is a p-h chart during the cooling main operation illustrated inFIG. 7. Injection operations in this mode will be described using FIG. 7and the p-h chart in FIG. 8.

Refrigerant suctioned into the compressor 10 and compressed by thecompressor 10 is condensed in the heat source side heat exchanger 12 tobecome high pressure two-phase gas-liquid refrigerant (point J in FIG.8). This high pressure two-phase gas-liquid refrigerant reaches thebranching unit 27 a via the check valve 13 a.

In the case of conducting injection, the opening and closing device 24closes, and part of the high pressure two-phase gas-liquid refrigerantbranched at the branching unit 27 a is made to flow into the suctioninjection pipe 4 c via the opening and closing device 24 and the branchpipe 4 d. The high pressure two-phase gas-liquid refrigerant flowinginto the suction injection pipe 4 c is depressurized by the expansiondevice 14 b to become a low temperature and low pressure two-phasegas-liquid refrigerant (point K in FIG. 8), and flows into a refrigerantpipe joining the compressor 10 and the accumulator 19.

Meanwhile, the remaining high pressure two-phase gas-liquid refrigerantbranched at the branching unit 27 a flows into the heat medium relayunit 3, is depressurized by the expansion devices 16 to become a lowpressure two-phase gas-liquid refrigerant, and then flows into theintermediate heat exchangers 15 which function as evaporators, becominga low temperature and low pressure gas refrigerant. After that, the lowtemperature and low pressure gas refrigerant returns to the outdoor unit1, and flows into the accumulator 19.

The low temperature and low pressure two-phase gas-liquid refrigerantflowing out from the suction injection pipe 4 c converges with the lowtemperature and low pressure gas refrigerant flowing out from theaccumulator 19 at a refrigerant pipe 4 connected on the suction side ofthe compressor 10 (point H in FIG. 8), and is suctioned into thecompressor 10. The low temperature and low pressure two-phase gas-liquidrefrigerant suctioned into the compressor 10 is heated and evaporated bythe hermetically sealed container and the motor of the compressor 10,becomes a low temperature and low pressure gas refrigerant at a lowertemperature than in the case of not conducting injection, is suctionedinto the compression chamber of the compressor 10, and is once againdischarged from the compressor 10 (point I in FIG. 8).

Note that in the case of not conducting injection, the opening andclosing device 24 closes, and the high pressure two-phase gas-liquidrefrigerant branched at the branching unit 27 a flows into the expansiondevice 16 b and the expansion device 16 a via the intermediate heatexchanger 15 b which functions as a condenser, becoming a low pressuretwo-phase gas-liquid refrigerant, and after flowing into theintermediate heat exchanger 15 a which functions as an evaporator andbecoming a low temperature and low pressure gas refrigerant, issuctioned into the compressor 10 via the accumulator 19 (point F in FIG.8). This low temperature and low pressure gas refrigerant is heated bythe hermetically sealed container and the motor of the compressor 10,becomes a low temperature and low pressure gas refrigerant at a highertemperature than in the case of conducting injection, is suctioned intothe compression chamber of the compressor 10, and is once againdischarged from the compressor 10 (point G in FIG. 8).

In addition, the temperature of refrigerant discharged from thecompressor 10 in the case of conducting injection (point I in FIG. 8)lowers with respect to the temperature of refrigerant discharged fromthe compressor 10 in the case of not conducting injection (point G inFIG. 8). In this way, even if the air-conditioning apparatus 100 employsa refrigerant whose discharge refrigerant temperature from thecompressor 10 reaches a high temperature (such as R32, for example), itis possible to lower the discharge refrigerant temperature of thecompressor 10, and improve the stability of the operation of theair-conditioning apparatus 100.

Note that the refrigerant in the flow path proceeding from the openingand closing device 24 in the branch pipe 4 d to the backflow preventiondevice 20 is high pressure refrigerant, whereas the refrigerant whichreturns to the outdoor unit 1 from the heat medium relay unit 3 via therefrigerant pipes 4 and reaches the branching unit 27 b is low pressurerefrigerant. Due to the action of the backflow prevention device 20, thehigh pressure refrigerant in the branch pipe 4 d is prevented frommixing with the low pressure refrigerant in the branching unit 27 b.Since refrigerant does not flow through the expansion device 14 a, anarbitrary opening degree may be set. The expansion device 14 b maycontrol the opening degree (expansion amount) such that the dischargerefrigerant temperature of the compressor 10 detected by the dischargerefrigerant temperature detection device 37 does not become too high.

Next, the flow of heat medium in the heat medium circuit B will bedescribed.

In the cooling main operation mode, the heating energy of therefrigerant is transferred to the heat medium in the intermediate heatexchanger 15 b, and the heated heat medium is made to flow inside thepipes 5 by the pump 21 b. Also, in the cooling main operation mode, thecooling energy of the refrigerant is transferred to the heat medium inthe intermediate heat exchanger 15 a, and the cooled heat medium is madeto flow inside the pipes 5 by the pump 21 a. The outflowing heat mediumpressurized by the pump 21 a and the pump 21 b flows into the use sideheat exchanger 26 a and the use side heat exchanger 26 b via the secondheat medium flow switching device 23 a and the second heat medium flowswitching device 23 b.

In the use side heat exchanger 26 b, the heat medium transfers heat tothe indoor air, thereby heating the indoor space 7. Also, in the useside heat exchanger 26 a, the heat medium takes away heat from theindoor air, thereby cooling the indoor space 7. At this point, the heatmedium is made to flow into the use side heat exchanger 26 a and the useside heat exchanger 26 b at a flow rate controlled by the action of theheat medium flow control device 25 a and the heat medium flow controldevice 25 b, this flow rate being the flow rate of heat medium necessaryto cover the air conditioning load required indoors. The heat mediumwith slightly lowered temperature passing through the use side heatexchanger 26 b goes through the heat medium flow control device 25 b andthe first heat medium flow switching device 22 b, flows into theintermediate heat exchanger 15 b, and is once again suctioned into thepump 21 b. The heat medium with slightly raised temperature passingthrough the use side heat exchanger 26 a goes through the heat mediumflow control device 25 a and the first heat medium flow switching device22 a, flows into the intermediate heat exchanger 15 a, and is once againsuctioned into the pump 21 a.

Meanwhile, each of the warm heat medium and the cool heat medium isintroduced into use side heat exchangers 26 having a heating load and acooling load, respectively, and due to the action of the first heatmedium flow switching devices 22 and the second heat medium flowswitching devices 23, the heat medium does not mix. Note that inside thepipes 5 of the use side heat exchangers 26, on both the heating side andthe cooling side, the heat medium flows in the direction going from thesecond heat medium flow switching devices 23 to the first heat mediumflow switching devices 22 via the heat medium flow control devices 25.In addition, the air conditioning load required in the indoor space 7may be covered by applying control to keep the difference between thetemperature detected by the first temperature sensor 31 b and thetemperature detected by the second temperature sensors 34 at a targetvalue on the heating side, while keeping the difference between thetemperature detected by the second temperature sensors 34 and thetemperature detected by the first temperature sensor 31 a at a targetvalue on the cooling side.

[Heating Main Operation Mode]

FIG. 9 is a diagram explaining the flow of refrigerant and heat mediumduring the heating only operation of the air-conditioning apparatus 100illustrated in FIG. 2. The heating main operation mode will be describedwith FIG. 9, taking as an example the case where a heating load isgenerated by the use side heat exchanger 26 a, and a cooling load isgenerated by the use side heat exchanger 26 b. Note that in FIG. 9,pipes indicated in bold represent pipes circulating refrigerant(refrigerant and a heat medium). Also, in FIG. 9, solid arrows indicatethe direction of refrigerant flow, while dashed arrows represent thedirection of heat medium flow.

In the case of the heating main operation mode illustrated in FIG. 9, inthe outdoor unit 1, the first refrigerant flow switching device 11switches such that refrigerant discharged from the compressor 10 flowsinto the heat medium relay unit 3 without passing through the heatsource side heat exchanger 12. In the heat medium relay unit 3, the pump21 a and the pump 21 b are driven, the heat medium flow control device25 a and the heat medium flow control device 25 b are fully opened, andthe heat medium flow control device 25 c and the heat medium flowcontrol device 25 d are fully closed, causing heat medium to circulatebetween each of the intermediate heat exchanger 15 a and theintermediate heat exchanger 15 b, and the use side heat exchanger 26 aand the use side heat exchanger 26 b, respectively.

First, the flow of refrigerant in the refrigerant circuit A will bedescribed.

Low temperature and low pressure refrigerant is compressed by thecompressor 10 to become high temperature and high pressure gasrefrigerant, and is discharged. The high temperature and high pressuregas refrigerant discharged from the compressor 10 goes through the firstrefrigerant flow switching device 11, is conducted through the firstconnecting pipe 4 a, passes through the check valve 13 b, and flows outfrom the outdoor unit 1 via the branching unit 27 a. The hightemperature and high pressure gas refrigerant flowing out of the outdoorunit 1 flows into the heat medium relay unit 3 via the refrigerant pipes4. The high temperature and high pressure gas refrigerant flowing intothe heat medium relay unit 3 goes through the second refrigerant flowswitching device 18 b, and flows into the intermediate heat exchanger 15b which acts as a condenser.

The gas refrigerant flowing into the intermediate heat exchanger 15 bcondenses and liquefies to become liquid refrigerant while transferringheat to the heat medium circulating through the heat medium circuit B.The liquid refrigerant flowing out of the intermediate heat exchanger 15b is expanded by the expansion device 16 b to become medium pressuretwo-phase refrigerant. This medium pressure two-phase refrigerant flowsvia the expansion device 16 a into the intermediate heat exchanger 15 a,which acts as an evaporator. The medium pressure two-phase refrigerantflowing into the intermediate heat exchanger 15 a evaporates by takingaway heat from the heat medium circulating through the heat mediumcircuit B, thus cooling the heat medium. This medium pressure two-phaserefrigerant flowing through the intermediate heat exchanger 15 a flowsout of the intermediate heat exchanger 15 a, flows out of the heatmedium relay unit 3 via the second refrigerant flow switching device 18a, and once again flows into the outdoor unit 1 via the refrigerantpipes 4.

The refrigerant flowing into the outdoor unit 1 flows into the secondconnecting pipe 4 b via the branching unit 27 b, goes through theexpansion device 14 a, is constricted by the expansion device 14 a tobecome low temperature and low pressure two-phase refrigerant, goesthrough the check valve 13 c, and flows into the heat source side heatexchanger 12 which acts as an evaporator. Then, the refrigerant flowinginto the heat source side heat exchanger 12 takes away heat from theoutside air at the heat source side heat exchanger 12, and becomes a lowtemperature and low pressure gas refrigerant. The low temperature andlow pressure gas refrigerant flowing out of the heat source side heatexchanger 12 is once again suctioned into the compressor 10 via thefirst refrigerant flow switching device 11 and the accumulator 19.

At this point, the opening degree of the expansion device 16 b iscontrolled such that the subcooling obtained as the difference betweenthe temperature detected by the third temperature sensor 35 b and avalue obtained by converting the pressure detected by the pressuresensor 36 into a saturation temperature becomes constant. Also, theexpansion device 16 a fully opens, while the opening and closing device17 a closes, and the opening and closing device 17 b closes. Note thatthe expansion device 16 b may fully open, and the subcooling may becontrolled with the expansion device 16 a.

[Heating Main Operation Mode p-h Chart]

FIG. 10 is a p-h chart during the heating main operation illustrated inFIG. 9. Injection operations in this mode will be described using FIG. 9and the p-h chart in FIG. 10.

Refrigerant suctioned into the compressor 10 and compressed by thecompressor 10 flows out of the outdoor unit 1 and is condensed by theintermediate heat exchanger 15 a of the heat medium relay unit 3, isdepressurized by the expansion device 16 a and the expansion device 16 bto reach medium pressure, and is evaporated by the intermediate heatexchanger 15 b to reach medium temperature (point J in FIG. 10), andflows from the heat medium relay unit 3 into the outdoor unit 1 via therefrigerant pipes 4. The medium temperature and medium pressurerefrigerant flowing into the outdoor unit 1 reaches the branching unit27 b.

In the case of conducting suction injection, the expansion device 14 bis opened to a predetermined opening degree, and part of the mediumtemperature and medium pressure two-phase gas-liquid refrigerantbranched at the branching unit 27 b is made to flow into the suctioninjection pipe 4 c via the branch pipe 4 d. The medium temperature andmedium pressure refrigerant flowing into the suction injection pipe 4 cis depressurized by the expansion device 14 b to become a lowtemperature and low pressure two-phase gas-liquid refrigerant (point Kin FIG. 10), and flows into a refrigerant pipe joining the compressor 10and the accumulator 19.

Meanwhile, the remaining medium temperature and medium pressuretwo-phase gas-liquid refrigerant branched at the branching unit 27 b isdepressurized by the expansion device 14 a to become a low pressuretwo-phase gas-liquid refrigerant, and then flows into the heat sourceside heat exchanger 12 which acts as an evaporator, becoming a lowtemperature and low pressure gas refrigerant. After that, the lowtemperature and low pressure gas refrigerant flows into the accumulator19.

The low temperature and low pressure two-phase gas-liquid refrigerantflowing out from the suction injection pipe 4 c converges with the lowtemperature and low pressure gas refrigerant flowing out from theaccumulator 19 at a refrigerant pipe 4 connected on the suction side ofthe compressor 10 (point H in FIG. 10), and is suctioned into thecompressor 10. The low temperature and low pressure two-phase gas-liquidrefrigerant is heated and evaporated by the hermetically sealedcontainer and the motor of the compressor 10, becomes a low temperatureand low pressure gas refrigerant at a lower temperature than in the caseof not conducting injection, is suctioned into the compression chamberof the compressor 10, and is once again discharged from the compressor10 (point I in FIG. 10).

Note that in the case of not conducting injection, the expansion device14 b closes, and the medium temperature and medium pressure two-phasegas-liquid refrigerant that passed through the branching unit 27 b isdepressurized by the expansion device 14 a to become a low pressuretwo-phase gas-liquid refrigerant, flows into the heat source side heatexchanger 12, which functions as an evaporator, to become a lowtemperature and low pressure gas refrigerant, and is suctioned into thecompressor 10 via the accumulator 19 (point F in FIG. 10). This lowtemperature and low pressure gas refrigerant is heated by thehermetically sealed container and the motor of the compressor 10,becomes a low temperature and low pressure gas refrigerant at a highertemperature than in the case of conducting injection, is suctioned intothe compression chamber of the compressor 10, and is once againdischarged from the compressor 10 (point Gin FIG. 10).

In addition, the temperature of refrigerant discharged from thecompressor 10 in the case of conducting injection (point I in FIG. 10)lowers with respect to the temperature of refrigerant discharged fromthe compressor 10 in the case of not conducting injection (point G inFIG. 10). In this way, even if the air-conditioning apparatus 100employs a refrigerant whose discharge refrigerant temperature from thecompressor 10 reaches a high temperature (such as R32, for example), itis possible to lower the discharge refrigerant temperature of thecompressor 10, and improve the stability of the operation of theair-conditioning apparatus 100.

Note that the opening and closing device 24 closes, preventing therefrigerant in a high pressure state from the branching unit 27 a frommixing with the refrigerant in a medium pressure state coming via thebackflow prevention device 20. Also, if the expansion device 14 aapplies control such that the medium pressure detected by the mediumpressure detection device 32 becomes a constant value, control of thedischarge refrigerant temperature from the expansion device 14 bstabilizes. Furthermore, the opening degree (expansion amount) of theexpansion device 14 b is controlled such that the discharge refrigeranttemperature of the compressor 10 detected by the discharge refrigeranttemperature detection device 37 does not become too high.

Also, in the heating main operation mode, it is necessary to cool heatmedium in the intermediate heat exchanger 15 b, and the pressure ofrefrigerant on the upstream side of the expansion device 14 a (mediumpressure) cannot be set very high. If medium pressure cannot be sethigh, the flow rate of refrigerant to inject on the suction side of thecompressor 10 decreases, and the discharge refrigerant temperature isnot lowered as much. However, this is not problematic. Since it isnecessary to prevent freezing of the heat medium, it may be configuredsuch that the system does not enter the heating main operation mode whenthe outside air temperature is low (for example, when the outside airtemperature is −5 degrees C. or less). When the outside temperature ishigh, the discharge refrigerant temperature is not very high, and theflow rate of suction injection does not need to be very large. With theexpansion device 14 a, cooling of the heat medium in the intermediateheat exchanger 15 b is also possible, and the medium pressure can be setto enable a supply a suction injection flow rate that is sufficient tolower the discharge refrigerant temperature. Thus, safer operation ispossible.

Next, the flow of heat medium in the heat medium circuit B will bedescribed.

In the heating main operation mode, the heating energy of therefrigerant is transferred to the heat medium in the intermediate heatexchanger 15 b, and the heated heat medium is made to flow inside thepipes 5 by the pump 21 b. Also, in the heating main operation mode, thecooling energy of the refrigerant is transferred to the heat medium inthe intermediate heat exchanger 15 a, and the cooled heat medium is madeto flow inside the pipes 5 by the pump 21 a. The outflowing heat mediumpressurized by the pump 21 a and the pump 21 b flows into the use sideheat exchanger 26 a and the use side heat exchanger 26 b via the secondheat medium flow switching device 23 a and the second heat medium flowswitching device 23 b.

In the use side heat exchanger 26 b, the heat medium takes away heatfrom the indoor air, thereby cooling the indoor space 7. Also, in theuse side heat exchanger 26 a, the heat medium transfer heat to theindoor air, thereby heating the indoor space 7. At this point, the heatmedium is made to flow into the use side heat exchanger 26 a and the useside heat exchanger 26 b at a flow rate controlled by the action of theheat medium flow control device 25 a and the heat medium flow controldevice 25 b, this flow rate being the flow rate of heat medium necessaryto cover the air conditioning load required indoors. The heat mediumwith slightly raised temperature passing through the use side heatexchanger 26 b goes through the heat medium flow control device 25 b andthe first heat medium flow switching device 22 b, flows into theintermediate heat exchanger 15 a, and is once again suctioned into thepump 21 a. The heat medium with slightly lowered temperature passingthrough the use side heat exchanger 26 a goes through the heat mediumflow control device 25 a and the first heat medium flow switching device22 a, flows into the intermediate heat exchanger 15 b, and is once againsuctioned into the pump 21 b.

Meanwhile, the warm heat medium and the cool heat medium is introducedinto use side heat exchangers 26 having a heating load and a coolingload, respectively, and due to the action of the first heat medium flowswitching devices 22 and the second heat medium flow switching devices23, the heat medium does not mix. Note that inside the pipes 5 of theuse side heat exchangers 26, on both the heating side and the coolingside, the heat medium flows in the direction going from the second heatmedium flow switching devices 23 to the first heat medium flow switchingdevices 22 via the heat medium flow control devices 25. In addition, theair conditioning load required in the indoor space 7 may be covered byapplying control to keep the difference between the temperature detectedby the first temperature sensor 31 b and the temperature detected by thesecond temperature sensors 34 at a target value on the heating side,while keeping the difference between the temperature detected by thesecond temperature sensors 34 and the temperature detected by the firsttemperature sensor 31 a at a target value on the cooling side.

Note that when executing the cooling only operation mode, the heatingonly operation mode, the cooling main operation mode, and the heatingmain operation mode, it is not necessary for the heat medium to flow touse side heat exchangers 26 with no heat load (including those switchedoff by thermo-off control). For this reason, the heat medium is made tonot flow to the use side heat exchangers 26 by closing flow paths withthe heat medium flow control devices 25.

In other words, the heat medium flow control devices 25 are controlledto fully open or fully close according to the heat load produced in theuse side heat exchangers 26.

[Compressor Protection Control]

FIG. 11 is a flowchart illustrating the operation of medium pressurecontrol, activation control, and steady-state control of theair-conditioning apparatus 100 according to Embodiment 1. Note that inthe following description, the expansion device 14 a and the expansiondevice 14 b are described as devices that have continuously variableopening degrees, such as electronic expansion valves driven by astepping motor, for example.

The air-conditioning apparatus 100 according to the present Embodiment 1is able to control the expansion device 14 a used for medium pressurecontrol and the expansion device 14 b used for discharge temperaturecontrol of the compressor 10 (compressor protection control) to enablethe effective injection of liquid refrigerant into the compressor 10irrespective of the operation mode.

The compressor protection control is broadly classified into mediumpressure control by the expansion device 14 a, steady-state control ofthe expansion device 14 b when the discharge refrigerant temperature ofthe compressor 10 transiently does not vary, and activation control ofthe expansion device 14 b when the discharge refrigerant temperature ofthe compressor 10 transiently rises.

Note that “transiently” refers to cases when the discharge refrigeranttemperature of the compressor 10 rises significantly, such as afteractivation of the compressor 10 or after returning from a defrostoperation.

(Medium Pressure Control)

The objectives of performing medium pressure control may be thefollowing, for example. In the case of a low outside air temperature,the evaporation temperature of the heat source side heat exchanger 12that functions as an evaporator falls, and if the discharge refrigeranttemperature of the compressor 10 becomes an extremely high temperatureor the density of the refrigerant suctioned into the compressor 10falls, the performance of the heating only operation mode and theheating main operation mode may decrease in some cases.

Consequently, by performing medium pressure control that regulates theopening degree of the expansion device 14 a, the refrigerant on theupstream side of the expansion device 14 a becomes medium pressurerefrigerant having a higher refrigerant pressure and a greater densitythan gas refrigerant or the like. Subsequently, by supplying the mediumpressure refrigerant to the suction injection pipe 4 c, decreaseddischarge refrigerant temperature of the compressor 10 when the outsideair temperature is low as well as decreased performance of the heatingonly operation mode and the heating main operation mode are minimized.

At this point, medium pressure will be described.

In the heating only operation mode, let low pressure refrigerant be therefrigerant flowing out from the heat source side heat exchanger 12, andlet high pressure refrigerant be the refrigerant supplied to theintermediate heat exchangers 15 a and 15 b. In this case, mediumpressure refers to a pressure that is less than the high pressure butgreater than the low pressure described herein.

In the heating main operation mode, let low pressure refrigerant be therefrigerant flowing out from the heat source side heat exchanger 12, andlet high pressure refrigerant be the refrigerant supplied to theintermediate heat exchanger 15 b. Medium pressure refers to a pressurethat is less than the high pressure but greater than the low pressuredescribed herein.

Medium pressure control is control that regulates the opening degree ofthe expansion device 14 a to set the refrigerant depressurized by theexpansion devices 16 to medium pressure, as described in the refrigerantflow of the refrigerant circuit A discussed earlier. The medium pressurecontrol corresponds to step A1 of FIG. 11, and is expressed morespecifically by the control method in FIG. 12 discussed later.

During the heating only operation mode, medium pressure control iscontrol that regulates the opening degree of the expansion device 14 aso that the opening degree becomes a preset target value, and sets thepressure of refrigerant on the upstream side of the expansion device 14a and the downstream side of the expansion device 16 a and the expansiondevice 16 b to medium pressure (see FIG. 5).

Also, during the heating main operation mode, medium pressure control iscontrol that regulates the opening degree of the expansion device 14 aso that the opening degree becomes a preset target value, and sets thepressure of refrigerant on the upstream side of the expansion device 14a and the downstream side of the expansion device 16 b to mediumpressure (see FIG. 9). Note that the opening degree of the expansiondevice 14 a is controlled so that the medium pressure detected by themedium pressure detection device 32 becomes a target value.

Furthermore, in medium pressure control during the cooling onlyoperation mode and cooling main operation mode, high pressure two-phasegas-liquid refrigerant flowing out from the heat source side heatexchanger 12 is supplied to the suction injection pipe 4 c via thebranching unit 27 a and the opening and closing device 24. Therefrigerant supplied to the suction injection pipe 4 c is depressurizedby the expansion device 14 b. Subsequently, liquid refrigerant issupplied to the suction side of the compressor 10.

Note that during the cooling only operation mode and cooling mainoperation mode, the refrigerant flowing out from the heat source sideheat exchanger 12 does not pass through the expansion devices 16, andthus is at high pressure. For this reason, during the cooling onlyoperation mode and cooling main operation mode, the opening degree ofthe expansion device 14 a is not particularly controlled, but insteadset to a fixed opening degree (for example, a fully open openingdegree), and the refrigerant supplied to the suction side of thecompressor 10 by the expansion device 14 b becomes low pressure.

(Steady-State Control)

Steady-state control is control that controls the opening degree of theexpansion device 14 b to minimize the risk of degradation ofrefrigerating machine oil and damage to the compressor 10 due to therefrigerant in the discharge part of the compressor 10 going to hightemperature. The steady-state control is performed when the dischargerefrigerant temperature of the compressor 10 does not transiently rise.

Note that the steady-state control may be performed in the cooling onlyoperation mode, the heating only operation mode, the cooling mainoperation mode, and the heating main operation mode, and controls theopening degree of the expansion device 14 b on the basis of a targetvalue of the discharge refrigerant temperature of the compressor 10(hereinafter also designated the target value Tdm of the dischargerefrigerant temperature). The steady-state control corresponds to stepA5 of FIG. 11, and is expressed more specifically by the control methodin FIG. 13 discussed later.

(Activation Control)

Activation control is similar to steady-state control in being controlthat controls the opening degree of the expansion device 14 b tominimize the risk of degradation of refrigerating machine oil and damageto the compressor 10 due to the refrigerant in the discharge part of thecompressor 10 going to high temperature. However, activation control isperformed instead of steady-state control when the discharge refrigeranttemperature transiently rises.

In cases such as immediately after activation of the compressor 10 orimmediately after returning from a defrost operation, the dischargerefrigerant temperature of the compressor 10 transiently changes from alow value to a high value, whereas the opening degree of the expansiondevice 14 b in this case is closed in the pre-activation state or thestate during the defrost operation.

In this way, if the opening degree of the expansion device 14 b does notincrease even though the discharge refrigerant temperature transientlyrises, there is a possibility of being unable to reliably minimizedegradation of refrigerating machine oil and damage to the compressor10. In other words, during activation of the compressor 10, although therefrigerant temperature transiently rises and may reach hightemperature, since the refrigerant temperature is not stable over timeand the discharge refrigerant temperature detection device 37 cannotdetect an accurate temperature, control to increase the opening degreeof the expansion device 14 b is not performed. For this reason, there isa possibility that the discharge refrigerant temperature of thecompressor 10 will go to high temperature and cause degradation ofrefrigerating machine oil and damage to the compressor 10.

Accordingly, in the activation control, the opening degree of theexpansion device 14 b is increased in cases such as immediately afteractivation of the compressor 10 or immediately after returning from adefrost operation.

Note that the degree to which the opening degree of the expansion device14 b increases is configured to be greater for the activation controlthan the steady-state control. More specifically, the value of thetarget value Tdm of the discharge refrigerant temperature for activationoperation is configured to be less than the target value Tdm of thedischarge refrigerant temperature for steady-state control (see step D2of FIG. 15 discussed later), thereby causing the opening degree of theexpansion device 14 b to become greater for activation control thansteady-state control. As a result, the quantity of liquid refrigerantsupplied to the compressor 10 increases, making it possible to rapidlydecrease the refrigerant temperature even if the discharge refrigeranttemperature of the compressor 10 transiently rises.

Note that similarly to the steady-state control, the activation controlmay be performed in the cooling only operation mode, the heating onlyoperation mode, the cooling main operation mode, and the heating mainoperation mode, and controls the opening degree of the expansion device14 b on the basis of the temperature of refrigerant discharged by thecompressor 10. The activation control corresponds to step A3 of FIG. 11,and is expressed more specifically by the control method in FIG. 15discussed later.

Next, a flow of medium pressure control, steady-state control, andactivation control in the compressor protection control will bedescribed with reference to FIG. 11. Note that the detailed content ofthe medium pressure control, the steady-state control, and theactivation control will be described later using FIGS. 12, 13, and 15.

<Step A0>

The controller 50 starts the compressor activation control due toactivation of the compressor 10.

The controller 50 sets the opening degree of the expansion device 14 ato an opening degree that does not generate medium pressure (forexample, fully open), and sets the opening degree of the expansiondevice 14 b to an opening degree that does not perform suction injection(for example, fully closed).

<Step A1>

The controller 50 proceeds to the medium pressure control by theexpansion device 14 a. The control in step A1 will be described indetail using FIG. 12.

<Step A2>

The controller 50 makes a determination on a start condition of theactivation control.

If the start condition of the activation control is satisfied, the flowproceeds to step A3.

If the start condition of the activation control is not satisfied, theflow proceeds to step A5.

Note that the start condition of activation control is decided on thebasis of the discharge refrigerant temperature of the compressor 10increasing significantly, such as after activation of the compressor 10or after returning from a defrost operation. Accordingly, the startcondition may be defined as (1) when a predetermined time elapses afteractivation of the compressor 10, or (2) when a predetermined timeelapses after returning from a defrost operation, for example.

<Step A3>

In step A3, activation control by the expansion device 14 b isperformed. The control in step A3 will be described in detail using FIG.15.

<Step A4>

The controller 50 makes a determination on an end condition of theactivation control.

If the end condition of the activation control is satisfied, the flowproceeds to step A5.

If the end condition of the activation control is not satisfied, theflow returns to step A3.

<Step A5>

The controller 50 performs steady-state control.

<Step A6>

The controller 50 ends the compressor activation control.

(Detailed Description of Medium Pressure Control)

FIG. 12 is a flowchart illustrating the operation of the medium pressurecontrol of the air-conditioning apparatus 100. The medium pressurecontrol by the expansion device 14 a will be described in detail withreference to FIG. 12.

<Step B0>

The controller 50 starts the medium pressure control by the expansiondevice 14 a.

The controller 50 sets the opening degree of the expansion device 14 ato an opening degree that does not generate medium pressure (forexample, fully open), and sets the opening degree of the expansiondevice 14 b to an opening degree that does not perform suction injection(for example, fully closed).

<Step B1>

The controller 50 determines whether or not the operation mode is theheating only operation mode or the heating main operation mode.

If the operation mode is one of these operation modes, the flow proceedsto step B2.

If the operation mode is not one of these operation modes, the flowproceeds to step B6.

<Step B2>

The controller 50 sets a medium pressure target value PMm.

Since heating only operation mode operates under an operating conditionof a lower outside air temperature than heating main operation, thedischarge refrigerant temperature correspondingly rises more readily,and the flow rate of refrigerant to inject into the suction side of thecompressor 10 increases. Accordingly, during the heating only operationmode, a higher medium pressure target value PMm compared to heating mainoperation mode may be set to increase the refrigerant flow rate. Forexample, the medium pressure target value PMm may be set to thesaturation pressure at 20 degrees C.

On the other hand, during the heating main operation mode, since any ofthe indoor units 2 a to 2 d are performing cooling operation, and theintermediate heat exchanger 15 a is functioning as an evaporator, themedium pressure cannot reach a very high value. For this reason, in theheating main operation mode, a lower medium pressure target value PMmcompared to heating only operation mode may be set. For example, themedium pressure target value PMm may be set to such as the saturationpressure from 0 to 10 degrees C.

Note that to smoothly change modes between the heating only operationmode and the heating main operation mode, the medium pressure targetvalue PMm in the heating only operation mode may be set to a value ofsimilar degree to the medium pressure target value PMm during theheating main operation mode.

<Step B3>

The controller 50 calculates an opening degree change amount ΔLEVa ofthe expansion device 14 a on the basis of the detection result of themedium pressure detection device 32 (hereinafter also designated themedium pressure detected value PM) and the medium pressure target valuePMm in step B2.

Note that the opening degree change amount ΔLEVa of the expansion device14 a is calculated according to the formula indicated in the followingEq. (1). Also, Eq. (1) expresses the opening degree change amount ΔLEVaof the expansion device 14 a as the value obtained by subtracting themedium pressure detected value PM of the medium pressure detectiondevice 32 from the medium pressure target value PMm, multiplied by acontrol gain Ga. Herein, the control gain Ga is a value determined bythe specifications of the expansion device 14 a.

<Step B4>

The controller 50 calculates the sum of the opening degree change amountΔLEVa calculated in step B3 and the previously output opening degreeLEVa* of the expansion device 14 a, as in Eq. (2) below. The value ofthe sum corresponds to the opening degree LEVa of the expansion device14 a.

Note that the previously output opening degree LEVa* of the expansiondevice 14 a refers to the value of the opening degree LEVa calculated instep B4 in the cycle performed one cycle previously to the cyclecurrently being performed, provided that one cycle is the compressorprotection control (see FIG. 11) that starts in step A0 and ends in stepA6.

<Step B5>

The controller 50 regulates the opening degree of the expansion device14 a to reach the opening degree LEVa of the expansion device 14 acalculated in step B4.

<Step B6>

The controller 50 sets the opening degree of the expansion device 14 ato a fixed opening degree (for example, fully open).

<Step B7>

The controller 50 ends the medium pressure control by the expansiondevice 14 a.

(Math. 1)

ΔLEVa=Ga×(PMm−PM)  (1)

(Math. 2)

LEVa=LEVa*+ΔLEVa  (2)

(Detailed Description of Steady-State Control)

FIG. 13 is a flowchart illustrating the operation of the steady-statecontrol of the air-conditioning apparatus 100. The steady-state controlby the expansion device 14 b performed when the discharge refrigeranttemperature of the compressor 10 does not transiently rise will bedescribed in detail with reference to FIG. 13.

<Step C0>

The controller 50 starts the steady-state control by the expansiondevice 14 b.

<Step C1>

The controller 50 sets a target value Tdm of the discharge refrigeranttemperature of the compressor 10.

For the description in FIG. 13, a case will be described in which thedischarge refrigerant temperature target value Tdm is set to 105 degreesC., for example.

<Step C2>

The controller 50 calculates an opening degree change amount ΔLEVb ofthe expansion device 14 b on the basis of the predetermined dischargerefrigerant temperature target value Tdm of step C1, and the detectionresult of the discharge refrigerant temperature detection device 37, orin other words the current value Td0 of the discharge refrigeranttemperature of the compressor 10.

Note that the opening degree change amount ΔLEVb of the expansion device14 b is calculated according to the formula indicated in the followingEq. (3). Also, Eq. (3) is expressed as the value obtained by subtractingthe current value Td0 of the discharge refrigerant temperature of thecompressor 10 from the discharge refrigerant temperature target valueTdm, multiplied by a control gain Gb. Herein, the control gain Gb is avalue determined by the specifications of the expansion device 14 b.

Note that step C2 herein is described as adopting a target value Tdm ofthe discharge refrigerant temperature of the compressor 10, but is notlimited thereto. For example, instead of the target value Tdm of thedischarge refrigerant temperature, a discharge degree of superheat ofthe compressor 10 obtained on the basis of the detected temperature fromthe discharge refrigerant temperature detection device 37 and thedetected pressure from the high pressure detection device 39 may also beused. In this way, not only the discharge refrigerant temperature butalso a factor related to the discharge refrigerant temperature, such asthe degree of superheat, may also be used.

In other words, in the present step C2, instead of the target value Tdmof the discharge refrigerant temperature, the opening degree changeamount ΔLEVb of the expansion device 14 b may also be calculated on thebasis of a target value of the discharge degree of superheat(corresponding to Tdm) which is a target value related to the dischargerefrigerant temperature, and a value of the discharge degree ofsuperheat related to the discharge refrigerant temperature(corresponding to Td0) obtained from the detected temperature from thedischarge refrigerant temperature detection device 37 and the detectedpressure from the high pressure detection device 39.

<Step C3>

The controller 50 calculates the sum of the opening degree change amountΔLEVb of the expansion device 14 b calculated using Eq. (3) and thepreviously output opening degree LEVb* of the expansion device 14 b, asin Eq. (4) below. The value of the sum corresponds to the opening degreeLEVb of the expansion device 14 b.

<Step C4>

The controller 50 regulates the opening degree of the expansion device14 b to reach the opening degree LEVb of the expansion device 14 bcalculated in step C3.

<Step C5>

The controller 50 ends the steady-state control by the expansion device14 b.

(Math. 3)

ΔLEVb=Gb×(Tdm−Td0)  (3)

(Math. 4)

LEVb=LEVb*+ΔLEVb  (4)

FIG. 14 is a graph for explaining three-point prediction. Although theopening degree change amount ΔLEVb of the expansion device 14 b iscalculated on the basis of Eq. (3), the configuration is not limitedthereto, and the three-point prediction discussed hereinafter may alsobe used.

In other words, rather than using the current value Td0 of the dischargerefrigerant temperature of the compressor 10 as in Eq. (3), the openingdegree change amount ΔLEVb of the expansion device 14 b may also becalculated using a three-point prediction that calculates a dischargerefrigerant temperature predicted value Tdn at the next control timing.

Three-point prediction is a method that assumes that various types ofresponse exhibit first-order lag characteristics, and from the values atthree different times, calculates a predicted value at the next time, oran endpoint value Tde that will be reached if the current statecontinues.

To describe the discharge refrigerant temperature of the compressor 10using FIG. 14 as an example, when first-order lag (the curve in FIG. 14)is expressed in the response of the discharge refrigerant temperature ofthe compressor 10 due to a change in the opening degree of the expansiondevice 14 b, the discharge refrigerant temperatures Td0, Td1, and Td2 atthree different times may be used to calculate a predicted value Tdn ofthe discharge refrigerant temperature at the next time in the formatindicated in Eq. (5) given below.

$\begin{matrix}\left( {{Math}.\mspace{14mu} 5} \right) & \; \\{{Tdn} = {{{Td}\; 0} + \frac{\left( {{{Td}\; 0} - {{Td}\; 1}} \right)^{2}}{{{Td}\; 1} - {{Td}\; 0}}}} & (5)\end{matrix}$

Herein, Td0 in Eq. (5) is the current value of the discharge refrigeranttemperature of the compressor 10, while Td1 is the discharge refrigeranttemperature of the compressor 10 at ΔT seconds before, and Td2 is thedischarge refrigerant temperature of the compressor 10 at (×T×2) secondsbefore. Herein, ΔT is set so that the control interval of the expansiondevice 14 b is (×T×3) seconds or greater.

To calculate the discharge refrigerant temperature predicted value Tdnof the compressor 10 at the next control timing using Eq. (5), the threeconditional expressions expressed in Eq. (6) must be satisfied.

(Math. 6)

Td0>Td1

and

Td1>Td2

and

Td0−Td1<Td1−Td2  (6)

In an actual operating state, the prediction does not necessarily yielda feasible operating state, and thus when the prediction is notpossible, the value calculated using Eq. (7) is used as the dischargerefrigerant temperature predicted value Tdn of the compressor 10 at thenext control timing.

(Math. 7)

Tdn=Td0+(Td0−Td1)  (7)

Note that the target value Tdm of the discharge refrigerant temperatureof the compressor 10 is required to be set as a value that is lower thanan upper-limit value of the discharge refrigerant temperature of thecompressor 10 set for the purpose of preventing degradation of therefrigerating machine oil or the like, but if it is set too low, thedischarge refrigerant temperature of the compressor 10 falls, and bothheating performance and cooling performance decreases.

Consequently, it is desirable to set the target value Tdm of thedischarge refrigerant temperature to as high a value as possible. Forexample, provided that the upper-limit value of the dischargerefrigerant temperature of the compressor 10 is 120 degrees C., a valuethat is 15 degrees C. lower, or 105 degrees C., may be set. AlthoughEmbodiment 1 describes an example of treating 105 degrees C. as thecontrol target value, the configuration is not limited thereto. Forexample, a value of approximately 100 degrees C. does not pose asignificant problem. To stop or slow down the compressor 10 at 110degrees C., the target value of the discharge refrigerant temperaturemay be set to a value from 100 to 110 degrees C.

Additionally, although the description of FIG. 14 describes a method ofpredicting the discharge refrigerant temperature of the compressor 10 aspart of the control in FIG. 13, this prediction method may also beapplied to the medium pressure as part of the control in FIG. 12. Inother words, the detection result of the medium pressure detectiondevice 32 may be predicted by three-point prediction, and in step B2 ofFIG. 12, the opening degree change amount ΔLEVa of the expansion device14 a may also be calculated on the basis of the predicted value of themedium pressure detection device 32, and the medium pressure targetvalue PMm in step B2.

(Detailed Description of Activation Control)

FIG. 15 is a flowchart illustrating the operation of activation controlof the air-conditioning apparatus 100 according to Embodiment 1. Theactivation control by the expansion device 14 b performed when thedischarge refrigerant temperature of the compressor 10 transiently riseswill be described in detail with reference to FIG. 15.

<Step D0>

The controller 50 proceeds to the activation control by the expansiondevice 14 b.

<Step D1>

The controller 50 sets a target value Tdm of the discharge refrigeranttemperature of the compressor 10.

In the activation control, the target value Tdm of the dischargerefrigerant temperature is set to a lower value than the target valueTdm of the discharge refrigerant temperature of the steady-statecontrol, and is set to a value such as 90 degrees C., for example. Notethat if the target value of the discharge refrigerant temperature duringsteady-state is set to a value from 100 to 110 degrees C., the targetvalue of the discharge refrigerant temperature in the activation controlmay be set to a lower value from 80 to 100 degrees C.

<Step D2>

The controller 50 calculates an opening degree change amount ΔLEVb ofthe expansion device 14 b on the basis of the predetermined dischargerefrigerant temperature target value Tdm of step D1, and the currentvalue Td0 of the discharge refrigerant temperature of the compressor 10.

Note that the opening degree change amount ΔLEVb of the expansion device14 b uses Eq. (3), similarly to step C2 discussed earlier.

Also, in the present step D2, the opening degree change amount ΔLEVblikewise may be calculated on the basis of a target degree of superheatrelated to the discharge refrigerant temperature and a current value ofthe discharge degree of superheat related to the discharge refrigeranttemperature, as discussed in step C2.

<Step D3>

The controller 50 calculates the sum of the calculated opening degreechange amount ΔLEVb of the expansion device 14 b and the previouslyoutput opening degree LEVb* of the expansion device 14 b, as in Eq. (4)above. The value of the sum corresponds to the opening degree LEVb ofthe expansion device 14 b.

<Step D4>

The controller 50 regulates the opening degree of the expansion device14 b to reach the opening degree LEVb of the expansion device 14 bcalculated in step D3.

In certain cases such as immediately after activating the compressor 10,the discharge refrigerant temperature Tdm is not stable, and thedetection result of the discharge refrigerant temperature detectiondevice 37 (the current value Td0 in step D1) takes a relatively lowvalue. However, in step D1, the target value Tdm of the dischargerefrigerant temperature is set to a lower value than the target valueTdm of the discharge refrigerant temperature of the steady-statecontrol. In other words, the current value Td0 more readily exceeds thetarget value Tdm of the discharge refrigerant temperature.

For this reason, immediately after the compressor 10 is activated, evenif the value of the opening degree LEVb* in step D3 is a first valuecorresponding to being fully closed, the value of the opening degreechange amount ΔLEVb in step D2 becomes a second value that increases theopening degree. In other words, after taking the sum of the first valueand the second value in step D3, a value that increases the openingdegree is output in step D4.

In this way, in the activation control, by setting the set value of thedischarge refrigerant temperature Tdm lower than in steady-statecontrol, the opening degree of the expansion device 14 b more readilybecomes greater than in steady-state control.

<Step D5>

The controller 50 determines whether or not the end condition in FIG. 16discussed later is satisfied.

If the end condition is satisfied, the flow proceeds to step D6.

If the end condition is not satisfied, the flow returns to step D2, andcontrol of the opening degree of the expansion device 14 b continues.

<Step D6>

The controller 50 ends the steady-state control by the expansion device14 b.

FIG. 16 is a graph illustrating the state of an end determination flagused in activation control of the air-conditioning apparatus 100according to Embodiment 1. The end condition of activation control(corresponding to step A4 of FIG. 11) will be described with referenceto FIG. 16. First, the definition of an activation control enddetermination flag flagA for determining whether or not to end theactivation control will be described using FIG. 16.

The definition of the activation control end determination flag flagA isdescribed below.

First, suppose that the end determination flag flagA=0 at activation orwhen defrosting ends.

Also, suppose that the end determination flag flagA=1 in the case inwhich the discharge refrigerant temperature Td of the compressor 10becomes equal to or greater than the target value Tdm of the dischargerefrigerant temperature when the end determination flag flagA=0 (point Ain FIG. 16).

Furthermore, suppose that the end determination flag flagA=2 in the casein which the discharge refrigerant temperature Td of the compressor 10becomes equal to or greater than the target value Tdm+α of the dischargerefrigerant temperature when the end determination flag flagA=1 (point Bin FIG. 16).

Herein, α is a threshold value to determine whether or not the dischargerefrigerant temperature has overshot the target value, and may be set to5 degrees C., for example.

Herein, suppose that the present activation control ends when either oneof the following two conditions is satisfied.

(1) The first condition is the case in which the end determination flagflagA=2 and Td<Tdm+β (Pattern 1 in FIG. 16).

(2) The second condition is the case in which the end determination flagflagA=1 and a predetermined time T has elapsed since flagA becameflagA=1 (Pattern 2 in FIG. 16).

Herein, β is a threshold value to determine whether or not a dischargerefrigerant temperature that overshot the discharge refrigeranttemperature target value+α has fallen back down. This threshold value βmust be set to a smaller value than the threshold value α discussedabove, and may be set to 3 degrees C., for example.

Also, the predetermined time T is a time used when determining whetheror not the state of performing the activation control is an operatingstate in which the discharge refrigerant temperature of the compressor10 rises, and may be set to a time such as 7 minutes, for example.Subsequently, the controller 50 determines that the dischargerefrigerant temperature of the compressor 10 is stable if the dischargerefrigerant temperature of the compressor 10 is low after the time Telapses.

When the activation control satisfies the end condition, the activationcontrol ends, and the flow proceeds to the steady-state control.

By conducting control as above, the discharge refrigerant temperaturemay be suitably controlled even when the discharge refrigeranttemperature of the compressor 10 greatly changes from a low value to ahigh value, such as at activation, and a highly reliableair-conditioning apparatus may be obtained.

Note that although the case in which the target value Tdm of thedischarge refrigerant temperature in the activation control is 90degrees C. has been described as an example, the configuration is notlimited thereto.

Provided that the upper limit of the discharge refrigerant temperatureof the compressor 10 is approximately 120 degrees C., the controller 50is configured to stop or slow down the compressor 10 if the dischargerefrigerant temperature reaches 110 degrees C., for example. In otherwords, since there is a high probability of damage to the compressor 10and the like if the refrigerant temperature reaches approximately 120degrees C., to protect the compressor 10, the compressor 10 is stoppedor slowed down before that point, at 110 degrees C.

At this point, if the target value Tdm of the discharge refrigeranttemperature is set to 105 degrees C. and the discharge refrigeranttemperature overshoots the discharge refrigerant temperature Tdm by 5degrees C. or more, protection of the compressor 10 starts, and thecompressor 10 is stopped or slowed down. For this reason, the targetvalue Tdm of the discharge refrigerant temperature may be set to atemperature lower than 105 degrees C. In this way, by providing aninterval greater than 5 degrees C. between the temperature at which thecompressor 10 is stopped or slowed down for protection (110 degrees C.)and the target value Tdm of the discharge refrigerant temperature (105degrees C.), the air-conditioning apparatus 100 becomes able to use thecompressor protection control more effectively.

Accordingly, the target value Tdm of the discharge refrigeranttemperature during the activation control may be set to 95 degrees C.,allowing for a discharge refrigerant temperature overshoot of 10 degreesC., or double 5 degrees C. Additionally, the target value Tdm of thedischarge refrigerant temperature may also be set to 90 degrees C. toprovide an even greater margin.

However, setting the target value Tdm of the discharge refrigeranttemperature to a temperature lower than 80 degrees C. means that moreliquid or two-phase refrigerant must be injected into the compressor 10to lower the discharge refrigerant temperature. In other words, aproblem occurs in that the expansion device 14 b opens too much, andproduces an excessive inflow of liquid or two-phase refrigerant into thecompressor 10.

Accordingly, the target value Tdm of the discharge refrigeranttemperature may be set to a temperature at which the compressor 10 doesnot enter discharge refrigerant temperature protection operation due toovershooting of the discharge refrigerant temperature of the compressor10 producing during the activation control, and at which the expansiondevice 14 b opens for injection (for example, approximately 90 degreesC. or 95 degrees C.).

In addition, by setting the opening degree of the expansion device 14 awhen starting the activation control to a value (such as fully open)that is larger than the opening degree in the steady state, the controltarget value may be reached quickly, and controllability may beimproved. In addition, by setting the opening degree of the expansiondevice 14 b when starting the activation control to a value (such asfully closed) that is smaller than the opening degree in the steadystate, the control target value may be reached quickly, andcontrollability may be improved.

In the activation control and the steady-state control of the expansiondevice 14 b, three-point prediction is described as an example of themethod of calculating a predicted value of the discharge refrigeranttemperature of the compressor 10, but the method of prediction is notlimited to three-point prediction, and a predicted value of thedischarge refrigerant temperature may also be computed using anotherprediction method.

Also, in the outdoor unit 1 according to the present embodiment, bylimiting the installation position of the branching unit 27 a to aposition on the refrigerant pipe 4 joining the heat source side heatexchanger 12 and the check valve 13 a as illustrated in FIG. 17, theopening and closing device 24 may be substituted with a backflowprevention device 24B, making it possible to configure theair-conditioning apparatus 100 at lower cost. Note that even with thecircuit layout in FIG. 17, the air-conditioning apparatus 100 isobviously still able to exhibit the same advantageous effects as thecircuit layout in FIG. 2.

[Advantageous Effects of Air-Conditioning Apparatus 100 According toEmbodiment 1]

The air-conditioning apparatus 100 according to Embodiment 1 performs asteady-state control and an activation control to regulate the openingdegree of the expansion device 14 b, thereby enabling medium pressurerefrigerant generated by the medium pressure control of the expansiondevice 14 a to be supplied to the suction injection pipe 4 c asappropriate. For this reason, it is possible to obtain a highly reliableair-conditioning apparatus 100 that improves operating stability bylowering the discharge refrigerant temperature Tdm of the compressor 10,irrespective of the operation mode.

Embodiment 2

FIG. 18 is a flowchart illustrating the operation of activation controlof the air-conditioning apparatus according to Embodiment 2. Note thatin the present Embodiment 2, the portions that differ from Embodiment 1primarily will be described.

Since the configuration of the refrigeration cycle and the flow ofrefrigerant and heat medium in the respective operation modes inEmbodiment 2 are the same as Embodiment 1, description thereof will bereduced or omitted.

The method of controlling the expansion device 14 b in the activationcontrol differs from Embodiment 1. Namely, the controller 50 performsthe control illustrated in FIG. 18 instead of the control in FIG. 15corresponding to step A3 of FIG. 11 in Embodiment 1. Note that themedium pressure control and the steady-state control are similar toEmbodiment 1.

[Activation Control Method 2]

The activation control method 2 by the expansion device 14 b performedwhen the discharge refrigerant temperature of the compressor 10transiently rises will be described in detail with reference to FIG. 18.

<Step E0>

The controller 50 proceeds to the activation control by the expansiondevice 14 b.

<Step E1>

The controller 50 determines whether or not the discharge refrigeranttemperature of the compressor 10 is equal to or greater than apredetermined temperature T2 (for example, 80 degrees C.).

In the case of determining that the discharge refrigerant temperature isequal to or greater than the temperature T2, the flow proceeds to stepE2. In the case of determining that the discharge refrigeranttemperature is not equal to or greater than the temperature T2, the flowproceeds to step E12.

<Step E2>

The controller 50 sets a target value Tdm of the discharge refrigeranttemperature of the compressor 10.

The target value Tdm of the discharge refrigerant temperature in theactivation control is set to a value such as 90 degrees C., for example.

<Step E3>

The controller 50 uses Eq. (6) to determine whether or not three-pointprediction is possible for the discharge refrigerant temperature of thecompressor 10.

In the case of determining that the conditions of Eq. (6) are satisfiedand three-point prediction is possible, the flow proceeds to step E5.

In the case of determining that the conditions of Eq. (6) are notsatisfied and three-point prediction is not possible, the flow proceedsto step E4.

<Step E4>

In the present step E4, which is the next control timing after step E3,the controller 50 again determines whether or not three-point predictionis possible for the discharge refrigerant temperature of the compressor10.

In the case of determining that three-point prediction is possible, theflow proceeds to step E5.

In the case of determining that three-point prediction is not possible,the flow proceeds to step E13.

<Step E5>

The controller 50 uses three-point prediction and Eq. (8) to calculate apredicted value that the discharge refrigerant temperature of thecompressor 10 is expected to reach. Note that the predicted valuereferred to herein is the endpoint value Tde (see FIG. 14) that will bereached if the current state continues when the discharge refrigeranttemperature is varying according to first-order lag characteristics.

$\begin{matrix}\left\lbrack {{Math}.\mspace{14mu} 8} \right\rbrack & \; \\{{Tde} = {{{Td}\; 2} + \frac{\left( {{{Td}\; 1} - {{Td}\; 2}} \right)^{2}}{{{- {Td}}\; 2} + {2 \times {Td}\; 1} - {{Td}\; 0}}}} & (8)\end{matrix}$

<Step E6>

The controller 50 calculates an opening degree change amount ΔLEVb ofthe expansion device 14 b on the basis of the predetermined dischargerefrigerant temperature target value Tdm of step E2, and the predictedvalue Tde from step E5.

Note that Eq. (9) is used to calculate the opening degree change amountΔLEVb of the expansion device 14 b in the present step E6. Herein, thecontrol gain Gb is a value determined by the specifications of theexpansion device 14 b.

(Math. 9)

ΔLEVb=Gb×(Tdm−Tde)  (9)

<Step E7>

The controller 50 calculates the sum of the calculated opening degreechange amount ΔLEVb of the expansion device 14 b and the previouslyoutput opening degree LEVb* of the expansion device 14 b, as in Eq. (4)above. The value of the sum corresponds to the opening degree LEVb ofthe expansion device 14 b.

<Step E8>

The controller 50 determines whether or not a control count of thenumber of times that the opening degree of the expansion device 14 b hasbeen output is less than a predetermined count N (for example, N=3).

If the control count is less than N, the flow returns to step E6.

If the control count is not less than N, or in other words equal to orgreater than N, the flow proceeds to step E9.

<Step E9>

If the output of the opening degree of the expansion device 14 b in stepE7 is the Nth time, the controller 50 starts a timer.

Note that in the present step E9, if the output of the opening degree isthe

(N+1)th time or greater, the timer has already started, and thus theflow proceeds to step E10 without performing any particular control.

<Step E10>

The controller 50 holds the opening degree of the expansion device 14 bfixed until the timer passes a predetermined time Te (for example, 15minutes).

<Step E11>

When the timer passes the time Te, the controller 50 ends the activationcontrol of FIG. 18, and proceeds to the steady-state control.

Also, if the discharge refrigerant temperature Td0 of the compressor 10exceeds the target value Tdm of the discharge refrigerant temperaturebefore the timer passes the predetermined time Te, the controller 50immediately ends the activation control and proceeds to the steady-statecontrol.

<Step E12>

After starting the activation control, the controller 50 holds theopening degree of the expansion device 14 b fixed in a fully closedstate until a predetermined time To elapses. After the time To elapses,the flow proceeds to step E13.

<Step E13>

The controller 50 ends the activation control by the expansion device 14b.

Note that the opening degree of the expansion device 14 b isincrementally controlled N times in step E8 in order to prevent thesystem from becoming unstable due to the opening degree of the expansiondevice 14 b varying greatly.

Herein, the opening degree is incrementally output three times, but theconfiguration is not limited thereto, and the calculated opening degreemay also be output directly without being incremented, insofar as thesystem does not become unstable.

[Advantageous Effects of Air-Conditioning Apparatus According toEmbodiment 2]

The air-conditioning apparatus according to Embodiment 2 performs anactivation control as discussed above, and exhibits advantageous effectssimilar to the air-conditioning apparatus 100 according to Embodiment 1.

Embodiment 3

FIG. 19 is a flowchart illustrating the operation of activation controlof the air-conditioning apparatus 100 according to Embodiment 3. Notethat in the present Embodiment 3, the portions that differ fromEmbodiments 1 and 2 primarily will be described.

Since the configuration of the refrigeration cycle and the flow ofrefrigerant and heat medium in the respective operation modes inEmbodiment 3 are the same as Embodiment 1, description thereof will bereduced or omitted. The method of controlling the expansion device 14 bin the activation control differs from Embodiment 1. Namely, thecontroller 50 performs the control illustrated in FIG. 19 instead of thecontrol in FIG. 15 corresponding to step A3 of FIG. 11 in Embodiment 1.Note that the medium pressure control and the steady-state control aresimilar to Embodiment 1.

[Activation Control Method 3]

The activation control method 3 by the expansion device 14 b performedwhen the discharge refrigerant temperature of the compressor 10transiently rises will be described in detail with reference to FIG. 19.

<Step F0>

The controller 50 proceeds to the activation control by the expansiondevice 14 b.

<Step F1>

The controller 50 determines whether or not the discharge refrigeranttemperature of the compressor 10 is equal to or greater than apredetermined temperature T2 (for example, 80 degrees C.).

In the case of determining that the discharge refrigerant temperature isequal to or greater than the temperature T2, the flow proceeds to stepF2.

In the case of determining that the discharge refrigerant temperature isnot equal to or greater than the temperature T2, the flow proceeds tostep F7.

<Step F2>

The controller 50 sets a target value Tdm of the discharge refrigeranttemperature of the compressor 10.

The target value Tdm of the discharge refrigerant temperature in theactivation control is set to a value such as 90 degrees C., for example.

<Step F3>

The controller 50 uses three-point prediction and Eq. (8) to calculate apredicted value that the discharge refrigerant temperature of thecompressor 10 is expected to reach. Note that the predicted valuereferred to herein is the endpoint value Tde (see FIG. 14) that will bereached if the current state continues when the discharge refrigeranttemperature is varying according to first-order lag characteristics.

If three-point prediction according to Eq. (8) is not possible, insteadof the endpoint value Tde of the discharge refrigerant temperature ofthe compressor 10 according to Eq. (8), the value calculated accordingto Eq. (10) may be treated as the endpoint value Tde of the dischargerefrigerant temperature of the compressor 10.

(Math. 10)

Tde=Td0+(Td0−Td1)  (10)

<Step F4>

The controller 50 calculates an opening degree change amount ΔLEVb ofthe expansion device 14 b on the basis of the predetermined dischargerefrigerant temperature target value Tdm of step F2, and the predictedvalue Tde from step F3.

Note that Eq. (9) is used to calculate the opening degree change amountΔLEVb of the expansion device 14 b in the present step F4.

<Step F5>

The controller 50 calculates the sum of the calculated opening degreechange amount ΔLEVb of the expansion device 14 b and the previouslyoutput opening degree LEVb* of the expansion device 14 b, as in Eq. (4)above. The value of the sum corresponds to the opening degree LEVb ofthe expansion device 14 b.

<Step F6>

The controller 50 determines whether or not the absolute value of thedifference between the target value Tdm of the discharge refrigeranttemperature of the compressor 10 and the current value Td0 of thedischarge refrigerant temperature of the compressor 10 is equal to orgreater than a predetermined temperature difference ΔT (for example, 3degrees C.).

If the absolute value of the difference is equal to or greater than thetemperature difference ΔT, the flow returns to step F3, and theactivation control continues.

If the absolute value of the difference is not equal to or greater thanthe temperature difference ΔT, or in other words less than thetemperature difference ΔT, the flow proceeds to step F8.

<Step F7>

After starting the activation control, the controller 50 holds theopening degree of the expansion device 14 b fixed in a fully closedstate until a predetermined time To elapses. After the time To elapses,the flow proceeds to step F8.

<Step F8>

The controller 50 ends the activation control by the expansion device 14b.

[Advantageous Effects of Air-Conditioning Apparatus 100 According toEmbodiment 3]

The air-conditioning apparatus 100 according to Embodiment 3 performs anactivation control as discussed above, and exhibits advantageous effectssimilar to the air-conditioning apparatus 100 according to Embodiments 1and 2.

Embodiment 4

FIG. 20 is a computational flowchart for computing the quality ofrefrigerant suctioned into the compressor 10 of the air-conditioningapparatus 100 according to Embodiment 4 of the present invention. Notethat in the present Embodiment 4, the portions that differ fromEmbodiments 1 to 3 primarily will be described.

For the compressor 10, it is conceivable to use a compressor that is alow-pressure shell type compressor which includes a compression chamberinside a hermetically sealed container, in which the inside of thehermetically sealed container is in a low-pressure refrigerant pressureenvironment, and that suctions and compresses low-pressure refrigerantinside the hermetically sealed container into the compression chamber.

Note that in the present Embodiment 4, a scroll compressor with alow-pressure shell structure is described as an example of thecompressor 10. When liquid or two-phase refrigerant is bypassed on thesuction side of the compressor 10 by suction injection, with alow-pressure shell-type compressor, the refrigerant suctioned into thecompressor 10 is sucked into the compression chamber after being heatedby the hermetically sealed container (that is, the shell). Consequently,even if an inflow of some liquid refrigerant into the compressor 10occurs, since the liquid refrigerant is heated and gasified by theshell, liquid refrigerant is not sucked into the compression chamber.

However, if the target value Tdm of the discharge refrigeranttemperature is set too low and the expansion device 14 b is opened toowide or depending on the operating state or the like, there is apossibility that an inflow of excessive liquid refrigerant into thecompressor 10 will occur, the liquid refrigerant will not besufficiently gasified by the heat of the shell, and liquid refrigerantwill be mixed with the refrigerant suctioned into the compressionchamber.

If liquid refrigerant is mixed with the refrigerant suctioned into thecompression chamber, inexpediences like the following may occur.

(1) If excessive liquid refrigerant that cannot be fully gasified by theheat of the shell of the compressor 10 is suctioned, liquid compressionthat compresses the incompressible liquid refrigerant inside thecompression chamber occurs, and there is a possibility that the scrollpart constituting the compression chamber may be damaged.

(2) If excessive liquid refrigerant accumulates in the bottom of theshell, the density of the refrigerating machine oil stored at the bottomof the shell falls, and the sliding member of the compressor 10 cannotbe fully lubricated, possibly leading to wear or damage of the slidingmember of the compressor 10.

Accordingly, when an inflow of excessive liquid refrigerant into thecompressor 10 occurs, it is necessary to reduce the opening degree ofthe expansion device 14 b to decrease the injection flow rate of liquidrefrigerant and protect the compressor 10.

In Embodiment 4, the determination of whether or not there is an inflowof excessive liquid refrigerant into the compressor 10 is made on thebasis of the computed value of the quality Xs (-) of refrigerant flowinginto the compressor 10. Accordingly, hereinafter, a method of computingthe quality Xs will be described taking the heating only operation modeas an example.

Note that (-) indicates a dimensionless quantity with no units.

<Step G0>

The controller 50 proceeds to the quality Xs computation control.

<Step G1>

The controller 50 detects the medium pressure PM (MPa) with the mediumpressure detection device 32, and detects the pressure Ps (MPa) of therefrigerant suctioned into the compressor 10 with the suction pressuredetection device 60.

<Step G2>

The controller 50 reads the current opening degrees LEVa and LEVb of theexpansion device 14 a and the expansion device 14 b. Note that theopening degree control of the expansion device 14 b is similar toEmbodiments 1 to 3.

<Step G3>

The controller 50 calculates an enthalpy H1 (kJ/kg) of refrigerantflowing out from the accumulator 19 on the basis of the pressure Ps(MPa) of suctioned refrigerant, and calculates an enthalpy H2 (kJ/kg) ofrefrigerant passing through the expansion device 14 b on the basis ofthe medium pressure PM (MPa).

Note that a detailed method of computing the enthalpy H1 and theenthalpy H2 (kJ/kg) will be discussed later.

<Step G4>

The controller 50 uses the opening degrees of the expansion device 14 aand the expansion device 14 b read in step G3 to compute an enthalpy H3(kJ/kg) of refrigerant suctioned into the compressor 10.

Note that a detailed method of computing the enthalpy H3 will bediscussed later.

<Step G5>

The controller 50 computes the quality Xs (-) of refrigerant suctionedinto the compressor 10 on the basis of the enthalpy H1 (kJ/kg), H2(kJ/kg), and H3 (kJ/kg) computed in step G4, and Eq. (19) below.

<Step G6>

The controller 50 ends the quality Xs computation control.

Next, a method of computing the enthalpy H3 in step G4 will be describedin detail.

The refrigerant flow rate G1 (kg/h) flowing out from the accumulator 19and the refrigerant flow rate G2 (kg/h) passing through the expansiondevice 14 b are decided by the Cv value of the expansion device 14 a andthe Cv value of the expansion device 14 b. The Cv value used herein isthe one typically used to express the capacity of an expansion device.

By using the Cv value, the refrigerant flow rate G1 (kg/h) flowing outfrom the accumulator 19 and the refrigerant flow rate G2 (kg/h) passingthrough the expansion device 14 b are respectively expressed in the formof Eq. (11) and Eq. (12), assuming that the pressure after passingthrough the expansion device 14 a is equal to the pressure of therefrigerant suctioned into the compressor 10. Herein, Cva and Cvb arethe Cv values of the expansion device 14 a and the expansion device 14b, respectively, while Ps (MPa) is the suction pressure of thecompressor 10 (a detected value from the suction pressure detectiondevice 60).

[Math. 11]

G1∝Cva√{square root over (PM−Ps)}  (11)

[Math. 12]

G2∝Cvb√{square root over (PM−Ps)}  (12)

Since the Cv value of an electronic expansion valve varies nearlyproportionally to the output pulse of the electronic expansion valve,Eq. (11) and Eq. (12) may be expressed as Eq. (13) and Eq. (14),respectively, provided that LEVa (-) is the opening degree of theexpansion device 14 a, and LEVb (-) is the opening degree of theexpansion device 14 b.

[Math. 13]

G1∝LEVa√{square root over (PM−Ps)}  (13)

[Math. 14]

G2∝LEVb√{square root over (PM−Ps)}  (14)

Next, provided that G1 (kg/h) and H1 (kJ/kg) are the flow rate andenthalpy, respectively, of refrigerant flowing out from the accumulator19, G2 (kg/h) and H2 (kJ/kg) are the flow rate and enthalpy,respectively, of refrigerant passing through the expansion device 14 b,and G3 (kg/h) and H3 (kJ/kg) are the flow rate and enthalpy,respectively, of refrigerant suctioned into the compressor 10, Eq. (15)is obtained by the law of conservation of energy.

(Math. 15)

G1×H1+G2×H2=(G1+G2)×H3  (15)

By substituting Eq. (13) and Eq. (14) into Eq. (15) and transforming theformula, the enthalpy H3 (kJ/kg) of the refrigerant suctioned into thecompressor 10 is expressed in the form of Eq. (16).

$\begin{matrix}\left\lbrack {{Math}.\mspace{14mu} 16} \right\rbrack & \; \\{{H\; 3} = {\frac{1}{{LEVa} + {LEVb}}\left( {{{LEVa} \times H\; 1} + {{LEVb} \times H\; 2}} \right)}} & (16)\end{matrix}$

In Eq. (16), since the opening degrees of the expansion device 14 a andthe expansion device 14 b are known, if the enthalpy H1 of refrigerantflowing out from the accumulator 19 and the enthalpy H2 of refrigerantpassing through the expansion device 14 b are known, the enthalpy H3(kJ/kg) of refrigerant suctioned into the compressor 10 may becalculated.

Herein, the enthalpy H1 (kJ/kg) of refrigerant flowing out from theaccumulator 19 is assumed to be saturated gas enthalpy, and the enthalpyH2 (kJ/kg) of refrigerant passing through the expansion device 14 b isassumed to be saturated liquid enthalpy.

Thus, with the detected value Ps (MPa) from the suction pressuredetection device 60, the enthalpy H1 (kJ/kg) of refrigerant flowing outfrom the accumulator 19 and the enthalpy H2 (kJ/kg) of refrigerantpassing through the expansion device 14 b may be calculated according toEq. (17) and Eq. (18)

indicated below. As a specific method, a table expressing pre-calculatedpressure and enthalpy relationships may be stored in the controller 50,and the table may be referenced.

(Math. 17)

H1=HG(Ps)  (17)

(Math. 18)

H2=HL(Ps)  (18)

According to the above, in step G4, the controller 50 is able tocalculate the enthalpies H1 (kJ/kg), H2 (kJ/kg), and H3 (kJ/kg) withEqs. (11) to (18). Subsequently, the controller 50 may calculate thequality Xs on the basis of the calculation results and Eq. (19) in thelater step G5.

(Math. 19)

Xs=(H3−H2)/(H1−H2)  (19)

Next, operation of the controller 50 in step G6 and thereafter will bedescribed.

The controller 50 calculates the quality Xs of refrigerant suctionedinto the compressor 10, and if the quality Xs of the refrigerantsuctioned into the compressor 10 is less than a predetermined value,determines that the amount of liquid refrigerant flowing into thecompressor 10 is excessive.

In other words, if the quality Xs of suctioned refrigerant of thecompressor 10 calculated according to Eq. (19) becomes less than a valuepredetermined to protect the compressor 10, the amount of liquidrefrigerant flowing into the compressor 10 is determined to be too much,and a protection control is conducted to, for example, decrease theopening degree of the expansion device 14 b (for example, set theopening degree to fully closed).

Furthermore, besides the control of the opening degree of the expansiondevice 14 b according to the quality Xs indicated in FIG. 20, if controlis performed utilizing the compressor shell temperature detection device61 as discussed next, damage to the compressor 10 may be more reliablyprevented, as discussed hereinafter.

When an excessive inflow of liquid or two-phase refrigerant into thecompressor 10 occurs, if, in addition to protection according to thequality Xs of refrigerant suctioned into the compressor 10 as discussedabove, protection using the detected value Tcomp from the compressorshell temperature detection device 61 provided in the bottom of theshell of the compressor 10 is introduced as a backup operation, damageto the compressor 10 may be more reliably prevented.

In this case, if the superheat at the bottom of the shell of thecompressor 10 (shell-bottom superheat) SHcomp, obtained by subtracting asaturation temperature Tsat calculated according to the detectedpressure of the suction pressure detection device 60 from the detectedvalue Tcomp of the compressor shell temperature detection device 61 asin Eq. (20), becomes less than a predetermined value (for example, 10degrees C.), an excessive inflow of liquid or two-phase refrigerant intothe compressor 10 is determined to have occurred, and a protectionoperation that stops or slows down the operation of the compressor 10may be conducted.

(Math. 20)

SHcomp=Tcomp−Tsat  (20)

Since the refrigerating machine oil accumulating at the floor of thecompressor 10 is sucked up along grooves or holes cut into the shaft ofthe motor and supplied to the scroll part as the motor of the compressor10 revolves, if an excessive inflow of liquid refrigerant into thecompressor 10 occurs, the refrigerating machine oil accumulating at thefloor of the compressor 10 is diluted by the liquid refrigerant, and asa result of the reduced density of the refrigerating machine oil, theviscosity of the refrigerating machine oil decreases.

If the viscosity of the refrigerating machine oil becomes less than aviscosity limit, the oil film thickness on the sliding member becomesthinner and the sliding member is worn away, potentially leading toannealing or damage to the compressor.

FIG. 21 illustrates the behavior of the mixed viscosity of R410Arefrigerant and an ester-based refrigerating machine oil of viscositygrade 30. The horizontal axis of FIG. 21 is the temperature of themixture of refrigerant and refrigerating machine oil, while the verticalaxis is the viscosity of the mixture of refrigerant and refrigeratingmachine oil. The viscosity at which insufficient lubrication occurscorresponds to the viscosity limit indicated in FIG. 21.

In FIG. 21, when the evaporating temperature is −20 degrees C., thelimit viscosity is reached at a temperature of −10 degrees C. for therefrigerant and refrigerating machine oil. When the evaporatingtemperature is −10 degrees C., the limit viscosity is reached at atemperature of 0 degrees C. for the refrigerant and refrigeratingmachine oil. In either state, the temperature difference obtained bysubtracting the evaporating temperature from the temperature of therefrigerant and refrigerating machine oil is 10 degrees C.,demonstrating that the viscosity of the refrigerating machine oilreaches the limit viscosity when the shell-bottom superheat of thecompressor 10 reaches 10 degrees C.

Consequently, in this case, protection operation may be started when theshell-bottom superheat of the compressor 10 becomes less than 10 degreesC. However, since the refrigerant mixture ratio and the mixed viscositydiffers depending on the type and viscosity grade of the refrigeratingmachine oil, the value at which to start the protection operationaccording to the shell-bottom superheat of the compressor 10 is notlimited to 10 degrees C., and an appropriate value may be used accordingto the combination of the above factors.

Although FIG. 21 illustrates the behavior of the mixed viscosity ofR410A refrigerant and an ester-based refrigerating machine oil ofviscosity grade 30, the types of refrigerant and refrigerating machineoil are not limited to the above. An ether-based or other type ofrefrigerating machine oil may be used, and a viscosity grade with avalue other than 30 does not pose a problem. In the case of usinganother refrigerant or refrigerating machine oil, the limit viscosityand the temperature at which to start the protection operation accordingto the shell-bottom superheat of the compressor 10 may be modifiedaccording to the change in the physical properties of the refrigerantand the refrigerating machine oil.

Experimental results demonstrate that for a typical low-pressure shellcompressor, in an operating state with a large rotational speed of thecompressor 10, a shell-bottom superheat of 10 degrees C. or greater maybe ensured if the quality Xs of refrigerant suctioned into thecompressor 10 is 0.90 or greater. Thus, the compressor 10 may beprotected if operation is conducted so that the quality Xs ofrefrigerant suctioned into the compressor 10 as computed in Eq. (19) isa value greater than 0.90. In other words, by causing wet refrigerantwith a quality Xs equal to or greater than 0.9 and less than or equal to0.99 to be suctioned into the compressor 10, the discharge refrigeranttemperature of the compressor 10 may be controlled while preventingdamage to the compressor 10. Note that since the amount of heat producedby the motor of the compressor 10 varies according to the compressionload and the rotational speed, the value at which an excessive quantityof liquid refrigerant is determined may be appropriately modifiedaccording to the compression load and the rotational speed.

Note that the present embodiment describes a case in which thecompressor 10 is a low-pressure shell-type compressor. In ahigh-pressure shell-type compressor in which the inside of ahermetically sealed container of the compressor 10 is in a high-pressurerefrigerant environment, refrigerant suctioned into the compressor 10flows into the compression chamber, and after beingcompressed/pressurized, is discharged into the compressor shell, andflows out from the compressor 10. In a high-pressure shell compressor,if the quality Xs of the suction refrigerant decreases and therefrigerant liquid component increases too much, there is a possibilitythat the compression mechanism will break. The quality limit at whichthe compression mechanism breaks is lower than the decrease in oilviscosity at the bottom of a low-pressure shell compressor in alow-pressure shell compressor, but if the quality Xs of refrigerantsuctioned into the compressor 10 is made to be equal to or greater than0.9 and less than or equal to 0.99, even a high-pressure shellcompressor may be reliably used safely.

[Advantageous Effects of Air-Conditioning Apparatus According toEmbodiment 4]

The air-conditioning apparatus according to Embodiment 4 minimizes thesupply of excessive liquid refrigerant to the compressor 10, and is ableto prevent the scroll part constituting the compression chamber frombeing damaged.

Since the air-conditioning apparatus according to Embodiment 4 minimizesthe supply of excessive liquid refrigerant to the compressor 10, theaccumulation of excessive liquid refrigerant at the bottom of the shellmay be minimized. For this reason, reductions in the density of therefrigerating machine oil are minimized, achieving minimal wear to thesliding member of the compressor 10, and preventing damage.

The air-conditioning apparatus according to Embodiments 1 to 4 is ableto inject refrigerant into the suction side of the compressor 10, andthus is able to moderate decreases in the stability of operation.

Also, the air-conditioning apparatus according to Embodiments 1 to 4 isable to conduct injection in the heating only operation mode, thecooling only operation mode, the heating main operation mode, and thecooling main operation mode. In other words, the air-conditioningapparatus according to Embodiments 1 to 4 is able to conduct injectioneven if the flow of refrigerant changes, such as by switching from thecooling operation to the heating operation or the cooling and heatingmixed operation or the like, for example.

Furthermore, the air-conditioning apparatus according to Embodiments 1to 4 enables injection with the addition of an improvement to therefrigerant circuit in the outdoor unit 1 and the heat medium relay unit3. In other words, the air-conditioning apparatus according toEmbodiments 1 to 4 is capable of injection even without a configurationsuch as one that provides a check valve or the like in the indoor units2, thus improving its versatility.

In the air-conditioning apparatus according to Embodiments 1 to 4, ifonly a heating load or a cooling load is generated in the use side heatexchangers 26, the corresponding first heat medium flow switchingdevices 22 and the second heat medium flow switching devices 23 are setto intermediate opening degrees to allow heat medium to flow throughboth the intermediate heat exchanger 15 a and the intermediate heatexchanger 15 b. Consequently, the use of both the intermediate heatexchanger 15 a and the intermediate heat exchanger 15 b may be used forthe heating operation or cooling operation, thereby increasing the heattransfer area and enabling efficient heating operation or coolingoperation to be conducted.

Also, in the case where a mixed heating load and cooling load isgenerated in the use side heat exchangers 26, the first heat medium flowswitching devices 22 and the second heat medium flow switching devices23 corresponding to the use side heat exchangers 26 switch to a flowpath connected to the intermediate heat exchanger 15 b used for heating,while the first heat medium flow switching devices 22 and the secondheat medium flow switching devices 23 corresponding to the use side heatexchangers 26 switch to a flow path connected to the intermediate heatexchanger 15 a used for cooling. In so doing, each indoor unit 2 is ableto freely conduct the heating operation and cooling operation.

Note that it is sufficient for the first heat medium flow switchingdevices 22 and the second heat medium flow switching devices 23 to bedevices able to switch flow paths, such as devices able to switch amonga three-way passage such as three-way valves, or a combination of twoopening and closing valves or other devices that open and close atwo-way passage. In addition, devices able to vary the flow rate in athree-way passage such as a mixing valve driven by a stepping motor, ora combination of two devices able to vary the flow rate in a two-waypassage such as an electronic expansion valve, may be used as the firstheat medium flow switching devices 22 and the second heat medium flowswitching devices 23. In this case, it is also possible to prevent awater hammer caused by the sudden opening or closing of a flow path.Furthermore, although the embodiments describe as an example the casewhere the heat medium flow control devices 25 are two-way valves, theheat medium flow control devices 25 may also be control valves having athree-way passage, and may be installed together with bypass pipes thatbypass the use side heat exchangers 26.

Also, besides a device able to vary an aperture surface area such as anelectronic expansion valve, an opening and closing valve such as acompact solenoid valve, a capillary tube, a compact check valve or thelike may also be used for the expansion device 14 a and the expansiondevice 14 b. Any device able to form medium pressure is sufficient.

Also, the heat medium flow control devices 25 may use a device driven bya stepping motor and able to control the flow rate flowing through aflow path, and may also be a two-way valve or a three-way valve with oneend sealed. Moreover, a device such as an opening and closing valve thatopens and closes a two-way passage may be used as the heat medium flowcontrol devices 25, with the average flow rate controlled by repeatedlyswitching the valve on and off.

In addition, although the second refrigerant flow switching devices 18are illustrated like four-way valves, the configuration is not limitedthereto, and refrigerant may be made to flow in the same way by usingmultiple two-way flow switching valves or three-way flow switchingvalves.

Also, a similar effect is obviously achieved even in the case where onlyone use side heat exchanger 26 and heat medium flow control device 25are connected. In addition, installing multiple intermediate heatexchangers 15 and expansion devices 16 that work the same obviouslyposes no problems. Furthermore, although the case of the heat mediumflow control devices 25 being housed inside the heat medium relay unit 3is described as an example, the configuration is not limited thereto,and the heat medium flow control devices 25 may also be housed insidethe indoor units 2, or configured separately from the heat medium relayunit 3 and the indoor units 2.

For the heat medium, substances such as brine (antifreeze), water, amixture of brine and water, or a mixture of water and a highlyanticorrosive additive may be used. Consequently, the air-conditioningapparatus according to Embodiments 1 to 4 contributes to improved safetyeven if the heat medium leaks into the indoor space 7 via the indoorunits 2, because a highly safe substance is used for the heat medium.

For the refrigerant, the effects of suction injection are large whenusing a refrigerant with a higher discharge refrigerant temperature suchas R32.

Besides R32, a refrigerant mixture (zeotropic refrigerant mixture) ofR32 and a tetrafluoropropene-based refrigerant with a low global warmingpotential such as HFO-1234yf expressed by the chemical formula CF3CF═CH2or HFO-1234ze expressed by the chemical formula CF3CH═CHF may be used.

In the case of using R32 as the refrigerant, the discharge refrigeranttemperature rises approximately 20 degrees C. compared to the case ofusing R410A in the same operating state, thus requiring usage oflowering the discharge refrigerant temperature, and the advantageouseffects of suction injection are large. For R410A, it is necessary tolower the discharge temperature by suction injection when using arefrigerant whose discharge refrigerant temperature rises even slightly,whereas for a refrigerant mixture of R32 and HFO-1234yf, in the casewhere the R32 mass ratio is 62% (62 wt %) or greater, the dischargerefrigerant temperature rises 3 degrees C. or more over the case ofusing R410A, and thus the advantageous effects are large if thedischarge refrigerant temperature is lowered by suction injection.

Also, for a refrigerant mixture of R32 and HFO-1234ze, in the case wherethe R32 mass ratio is 43% (43 wt %) or greater, the dischargerefrigerant temperature rises 3 degrees C. or more over the case ofusing R410A, and thus the advantageous effects are large if thedischarge refrigerant temperature is lowered by suction injection.

Also, the refrigerant types in the refrigerant mixture are not limitedto these, and a refrigerant mixture containing small quantities of otherrefrigerant components does not largely affect the discharge refrigeranttemperature, and exhibits similar advantageous effects. For example, arefrigerant mixture of R32 and HFO-1234yf that also contains smallquantities of other refrigerants may still be used.

In addition, although fans are typically installed in the heat sourceside heat exchanger 12 and the use side heat exchangers 26 a to 26 d topromote condensation or evaporation by blowing air, the configuration isnot limited thereto. For example, devices such as panel heatersutilizing radiation may also be used as the use side heat exchangers 26a to 26 d, while a water-cooled device that moves heat with water orantifreeze may be used as the heat source side heat exchanger 12. Anydevice may be used insofar as the device has a structure enabling heatto be given off or taken way.

Also, although the description herein takes the case of four use sideheat exchangers 26 a to 26 d as an example, any number thereof may beconnected.

In addition, although the case of two intermediate heat exchangers 15 aand 15 b is described as an example, the configuration is obviously notlimited thereto, and any number of intermediate heat exchangers 15 maybe installed insofar as the configuration enables the cooling and/orheating of heat medium.

In addition, the pumps 21 a and 21 b are not limited to one each, andmultiple low-capacity pumps may also be arranged in parallel.

Also, in the present embodiments, an exemplary configuration like thefollowing is described. Namely, a compressor 10, a four-way valve (firstrefrigerant flow switching device) 11, a heat source side heat exchanger12, an expansion device 14 a, an expansion device 14 b, an opening andclosing device 24, and a backflow prevention device 20 are housed in anoutdoor unit 1. Also, the use side heat exchangers 26 are housed in theindoor units 2, while the intermediate heat exchangers 15 and theexpansion devices 16 are housed in the heat medium relay unit 3.Furthermore, the outdoor unit 1 and the heat medium relay unit 3 areinterconnected by a pair of pipes, with refrigerant circulated betweenthe outdoor unit 1 and the heat medium relay unit 3, while the indoorunits 2 and the heat medium relay unit 3 are interconnected byrespective pairs of pipes, with heat medium circulated between theindoor units 2 and the heat medium relay unit 3. Heat is exchangedbetween the refrigerant and the heat medium at the intermediate heatexchangers 15. However, the air-conditioning apparatus according toEmbodiments 1 to 4 is not limited thereto.

For example, it is also possible to apply the present invention to, andexhibit similar advantageous effects with, a direct expansion system inwhich the compressor 10, the four-way valve (first refrigerant flowswitching device) 11, the heat source side heat exchanger 12, theexpansion device 14 a, the expansion device 14 b, the opening andclosing device 24, and the backflow prevention device 20 are housed inthe outdoor unit 1, while load side heat exchangers, which exchange heatbetween the air of the air-conditioned space and the refrigerant, andthe expansion devices 16 are housed in the indoor units 2. A relay unitformed separately from the outdoor unit 1 and the indoor units 2 isprovided, with the outdoor unit 1 and the relay unit interconnected by apair of pipes, and with the indoor units 2 and the relay unitinterconnected by respective pairs of pipes. Refrigerant is circulatedbetween the outdoor unit 1 and the indoor units 2 via the relay unit,enabling the cooling only operation, the heating only operation, thecooling main operation, and the heating main operation to be conducted.

Also, in the present embodiments, an exemplary configuration like thefollowing is described. Namely, a compressor 10, a four-way valve (firstrefrigerant flow switching device) 11, a heat source side heat exchanger12, an expansion device 14 a, and an expansion device 14 b are housed inan outdoor unit 1. Also, use side heat exchangers 26 are housed inindoor units 2. Furthermore, intermediate heat exchangers 15 andexpansion devices 16 are housed in a heat medium relay unit 3, and theoutdoor unit 1 and the heat medium relay unit 3 are interconnected by apair of pipes, with refrigerant circulated between the outdoor unit 1and the heat medium relay unit 3, while the indoor units 2 and the heatmedium relay unit 3 are interconnected by respective pairs of pipes,with heat medium circulated between the indoor units 2 and the heatmedium relay unit 3. Heat is exchanged between the refrigerant and theheat medium at the intermediate heat exchangers 15. However, theair-conditioning apparatus according to Embodiments 1 to 4 is notlimited thereto.

For example, it is also possible to apply the present invention to, andexhibit similar advantageous effects with, a direct expansion system inwhich the compressor 10, the four-way valve (first refrigerant flowswitching device) 11, the heat source side heat exchanger 12, theexpansion device 14 a, and the expansion device 14 b are housed in theoutdoor unit 1, while load side heat exchangers, which exchange heatbetween the air of the air-conditioned space and the refrigerant, andthe expansion devices 16 are housed in the indoor units 2. Multipleindoor units are connected to the outdoor unit 1 by pairs of pipes, andthe refrigerant is circulated between the outdoor unit 1 and the indoorunits 2, enabling the cooling operation and the heating operation to beconducted.

Also, although an air-conditioning apparatus capable of the cooling andheating mixed operation, such as the cooling main operation and theheating main operation, is described as an example herein, theconfiguration is not limited thereto. The present invention may also beapplied to, and similar advantageous effects exhibited with, anair-conditioning apparatus unable to conduct the cooling and heatingmixed operation that switches between the cooling only operation and theheating only operation. Also, devices provided with just oneintermediate heat exchanger are included among devices that are unableto conduct the cooling and heating mixed operation.

1. An air-conditioning apparatus, including a compressor, a refrigerant flow switching device, a heat source side heat exchanger, a first expansion device, and an intermediate heat exchanger connected via refrigerant pipes, that constitutes a refrigerant circuit, and a pump, the intermediate heat exchanger, and a use side heat exchanger connected via pipes, that constitutes a heat medium circuit B, the air-conditioning apparatus comprising: a second expansion device provided on an upstream side of the heat source side heat exchanger during a heating operation; an accumulator configured to accumulate excess refrigerant provided on an upstream side of the compressor; a suction injection pipe, having one end connected on an upstream side of the second expansion device during the heating operation, and another end connected to a flow channel between a suction side of the compressor and the accumulator; a third expansion device provided to the suction injection pipe; a discharge refrigerant temperature detector configured to detect a discharge refrigerant temperature of the compressor; and a controller configured to control an opening degree of the second expansion device and/or the third expansion device based on at least a detection result from the discharge refrigerant temperature detector; wherein, inside the refrigerant pipes, a refrigerant having a higher discharge refrigerant temperature than R410A is circulated as refrigerant, the controller, during the heating operation, performs discharge temperature control that controls an opening degree of the third expansion device based on a deviation between one of a target value of the discharge refrigerant temperature and a target value related to the discharge refrigerant temperature, and any one of the discharge refrigerant temperature detected by the discharge refrigerant temperature detector, a value related to the discharge refrigerant temperature computed using the detected discharge refrigerant temperature, and a predicted value of the discharge refrigerant temperature or of a value related to the discharge refrigerant temperature computed using the detected discharge refrigerant temperature, and causes refrigerant having a quality equal to or greater than 0.9 and less than or equal to 0.99 to be suctioned into the compressor.
 2. The air-conditioning apparatus of claim 1, wherein R32 or a refrigerant mixture with an R32 mass ratio of 62% or greater is circulated as the refrigerant.
 3. The air-conditioning apparatus of claim 1, comprising: a medium pressure detector configured to detect a refrigerant pressure or a refrigerant saturation temperature on an upstream side of the second expansion device during the heating operation; wherein the controller during the heating operation, performs medium pressure control that controls the opening degree of the second expansion device based on a deviation between a target value of medium pressure and a detection result of the medium pressure detector or a predicted value.
 4. The air-conditioning apparatus of claim 3, further comprising: a high pressure detector configured to detect a pressure of refrigerant discharged from the compressor; wherein the controller calculates a degree of superheat of refrigerant discharged from the compressor based on a detection result of the discharge refrigerant temperature detector and the high pressure detector, and sets the degree of superheat as a target value related to the discharge refrigerant temperature.
 5. The air-conditioning apparatus of claim 1, wherein the controller sets the opening degree of the second expansion device to a fixed opening degree during a cooling operation.
 6. The air-conditioning apparatus of claim 1, wherein the controller, during the cooling operation, causes refrigerant having a quality equal to or greater than 0.9 and less than or equal to 0.99 to be suctioned into the compressor.
 7. The air-conditioning apparatus of claim 1, wherein the controller takes a target value of a discharge refrigerant temperature of the compressor to be a value from 100 degrees C. to 110 degrees C., and controls the discharge refrigerant temperature of the compressor to approach the target value of the discharge refrigerant temperature.
 8. The air-conditioning apparatus of claim 1, wherein the controller includes activation control that differs from control during a steady state, in which the activation control is performed after the compressor is activated until a predetermined condition is satisfied, and takes a target value of a discharge refrigerant temperature during the activation control to be a value from 80 degrees C. to 100 degrees C., and controls the discharge refrigerant temperature of the compressor to approach the target value of the discharge refrigerant temperature.
 9. The air-conditioning apparatus of claim 8, wherein the controller ends the activation control in a case of judging that the discharge refrigerant temperature of the compressor sufficiently approached the target value of discharge refrigerant temperature during activation control.
 10. The air-conditioning apparatus of claim 1, wherein the compressor includes a compression chamber inside a hermetically sealed container, and is a compressor with a low-pressure shell structure in which an inside of the hermetically sealed container is in a low-pressure refrigerant pressure environment that suctions and compresses low-pressure refrigerant inside the hermetically sealed container into the compression chamber, includes a compressor shell temperature detector configured to detect a temperature on a lower side of the hermetically sealed container, and the controller causes the compressor to stop or causes the compressor to slow down when one of a detection result of the compressor shell temperature detector and a value computed from a detection result of the compressor shell temperature detector falls below a predetermined value.
 11. The air-conditioning apparatus of claim 1, comprising: a first refrigerant branching unit that, during the cooling operation, diverts the refrigerant from a refrigerant flow path when the refrigerant is flowing from the heat source side heat exchanger to the first expansion device; a second refrigerant branching unit that, during the heating operation, diverts the refrigerant from a refrigerant flow path when the refrigerant is flowing from the first expansion device to the heat source side heat exchanger; a branch pipe that connects the first refrigerant branching unit and the second refrigerant branching unit, with the suction injection pipe connected thereto, a first conducting device installed between the first refrigerant branching unit and a joint between the branch pipe and the suction injection pipe; and a second conducting device installed between the second refrigerant branching unit and the joint.
 12. The air-conditioning apparatus of claim 11, wherein action of the refrigerant flow switching device enables a cooling operation causing high pressure refrigerant to flow into the heat source side heat exchanger serving as a condenser, and causing low pressure refrigerant to flow into some or all of the intermediate heat exchangers serving as evaporators, and during the cooling operation, the refrigerant circulates through the refrigerant circuit without going through the second expansion device, enabling the high pressure refrigerant to be introduced on a suction side of the compressor via the first conducting device, the third expansion device, and the suction injection pipe.
 13. The air-conditioning apparatus of claim 11, wherein the first refrigerant branching unit is disposed at a position where the refrigerant flows in from respectively different directions during the cooling operation and the heating operation, the second refrigerant branching unit is disposed at a position where the refrigerant flows in from a same direction during the cooling operation and the heating operation, the first conducting device is a backflow prevention device that conducts the refrigerant only in a direction flowing from the first refrigerant branching unit to the suction injection pipe, and the second conducting device is a backflow prevention device that conducts the refrigerant only in a direction flowing from the second refrigerant branching unit to the suction injection pipe.
 14. The air-conditioning apparatus of claim 1, wherein the controller computes a quality of refrigerant suctioned into the compressor, and when the quality is less than a predetermined value, determines that too much liquid refrigerant is flowing into the compressor, and reduces the opening degree of the third expansion device. 